EP1762793A2 - Kühler mit geschlossenem Luftkreislauf und dessen Kühlverfahren - Google Patents

Kühler mit geschlossenem Luftkreislauf und dessen Kühlverfahren Download PDF

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Publication number
EP1762793A2
EP1762793A2 EP06003379A EP06003379A EP1762793A2 EP 1762793 A2 EP1762793 A2 EP 1762793A2 EP 06003379 A EP06003379 A EP 06003379A EP 06003379 A EP06003379 A EP 06003379A EP 1762793 A2 EP1762793 A2 EP 1762793A2
Authority
EP
European Patent Office
Prior art keywords
refrigerant
cooled
heat exchanger
expansion turbine
circulating pipe
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
EP06003379A
Other languages
English (en)
French (fr)
Other versions
EP1762793A3 (de
EP1762793B1 (de
Inventor
Masato Mitsuhashi
Seiichi Okuda
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.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Ltd
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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP1762793A2 publication Critical patent/EP1762793A2/de
Publication of EP1762793A3 publication Critical patent/EP1762793A3/de
Application granted granted Critical
Publication of EP1762793B1 publication Critical patent/EP1762793B1/de
Expired - Fee Related 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
    • 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
    • F25B9/004—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 air
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING OR HOLDING
    • B25B9/00—Hand-held gripping tools other than those covered by group B25B7/00

Definitions

  • the present invention relates to a closed type air refrigerant refrigerator, more particularly, to a closed type air refrigerant refrigerator and a cooling method using the same.
  • FIG. 1 is a schematic diagram showing a configuration of the conventional opened type air refrigerant refrigerator (direct cooling type).
  • a compressor 3 compresses air refrigerant sucked from the atmosphere.
  • a first heat exchanger 5 carries out heat exchange between the air compressed by the compressor 3 and an atmosphere, and a second heat exchanger 6 further cools the air refrigerant cooled by the first heat exchanger by carrying out heat exchange with a low temperature air refrigerant outputted from a refrigeration storage.
  • An expansion turbine 4 adiabatically expands the cooled air cooled by the second hear exchanger 6 and further cools the cooled air.
  • the compressor 3 and the expansion turbine 4 are fixed to a rotational shaft of a motor 2.
  • the air as the refrigerant sucked from the atmosphere is directly cooled and the cooled air refrigerant keeps a refrigeration target 7 such as refrigeration objects cool.
  • the refrigeration target 7 has a door 7a, and refrigeration objects are carried in or out through the door 7a.
  • air within the refrigeration target 7 is replaced with outside air as appropriate.
  • a closed type air refrigerant refrigerator 10 shown in Fig. 2 is proposed.
  • air as refrigerant is taken into a circulating line 18 of the air refrigerant from the atmosphere via a shut valve 19.
  • a compressor 13 compresses the air refrigerant sucked from the atmosphere.
  • a first heat exchange system 15 carries out heat exchange between the air compressed by the compressor 13 and the atmospheric, and a second heat exchange system 16 further cools the air refrigerant cooled by the first heat exchange system 15 by carrying out heat exchange with low temperature air refrigerant outputted from a refrigeration storage 17.
  • An expansion turbine 12 adiabatically expands the air refrigerant cooled by the second hear exchanger 16 and cools the air refrigerant to about -75°C.
  • the compressor 13 and the expansion turbine 12 are rotated with a driving force by a motor 11. As shown in Fig. 2, in this conventional closed type air refrigerant refrigerator shown in Fig.
  • the air refrigerant is taken from the atmosphere into a pipe line and is hermetically closed in the pipe line 18 to have a pressure corresponding to an operating environment.
  • a refrigeration storage 17 is kept due to the cooled air refrigerant via a third heat exchange system 14.
  • the closed type air refrigerant refrigerator 10 can carry out a stable cooling operation without being affected by the operation environment such as atmospheric pressure and change in atmospheric pressure).
  • An object of the present invention is to provide a closed type air refrigerant refrigerator, which uses dry air or nitrogen gas containing no moisture and has a mechanism for preventing refrigerant filled in a pipe from directly contacting atmosphere.
  • a closed type refrigerator includes a motor having a rotation shaft; a compressor coupled to one end of the rotation shaft; an expansion turbine coupled to the other end of the rotation shaft; a refrigerant circulating pipe configured to circulate a refrigerant from an outlet of the compressor and an inlet of the expansion turbine and from an outlet of the expansion turbine to an inlet of the compressor to form a closed loop for a flow route of the refrigerant; a first heat exchanger provided in a portion of the refrigerant circulating pipe from the outlet of the compressor to the inlet of the expansion turbine; and a second heat exchanger provided in a portion of the refrigerant circulating pipe from the first heat exchanger to the inlet of the expansion turbine.
  • the compressor compresses the refrigerant
  • the first heat exchanger carries out heat exchange between the compressed refrigerant and atmosphere to generate a first cooled refrigerant.
  • the second heat exchanger carries out heat exchange between the first cooled refrigerant and a second cooled refrigerant to generate a third cooled refrigerant, and the expansion turbine adiabatically expands the third cooled refrigerant to generate the second cooled refrigerant, which is used to cool a refrigeration storage and supplied to the inlet of the compressor.
  • the refrigerant is dehumidified and is hermetically closed in the refrigerant circulating pipe such that the refrigerant does not condense even when the refrigerant is cooled to a minimum temperature in the refrigerant circulating pipe.
  • the refrigerant may be dry air or dry nitrogen.
  • the closed type refrigerator may further include a brine heat exchanger provided in a portion of the refrigerant circulating pipe between the outlet of the expansion turbine and the second heat exchanger to carry out heat exchange between the second cooled refrigerant and a brine in a brine line.
  • a portion the brine line is arranged in the refrigeration storage.
  • a portion of the refrigerant circulating pipe from the outlet of the expansion turbine to the second heat exchanger may be arranged in the refrigeration storage.
  • a method of cooling a refrigeration storage is achieved by compressing a refrigerant by compressor, wherein the compressor is coupled to one end of a rotation shaft of a motor, and the refrigerant is dehumidified and is hermetically closed in a refrigerant circulating pipe such that the refrigerant does not condense even when the refrigerant is cooled to a minimum temperature in the refrigerant circulating pipe; by circulating the compressed refrigerant in the refrigerant circulating pipe to a first heat exchanger; by carrying out heat exchange between the compressed refrigerant and atmosphere by the first heat exchanger to generate a first cooled refrigerant; by circulating the first cooled refrigerant in the refrigerant circulating pipe to a second heat exchanger; by carrying out second heat exchange between the first cooled refrigerant and a second cooled refrigerant by the second heat exchanger to generate a third cooled refrigerant; by adiabatically expanding the third cooled refrigerant
  • the refrigerant may be dry air or dry nitrogen.
  • the cooling may be achieved by carrying out a brine heat exchange between the second cooled refrigerant and a brine in a brine line between the expansion turbine and the second heat exchanger. A portion the brine line is arranged in the refrigeration storage.
  • a portion of the refrigerant circulating pipe from the expansion turbine to the second heat exchanger is arranged in the refrigeration storage.
  • Fig. 3 is a schematic diagram showing the configurations of the closed type air refrigerant refrigerator according to the first embodiment of the present invention.
  • the air refrigerant refrigerator 20 is provided with a compressor 3 and an expansion turbine 4.
  • the compressor 3 is coupled to an end of a shaft of a motor 2 and the expansion turbine 4 is coupled to the other end of the shaft.
  • a refrigerant circulating pipe 21 is connected to the inlet of the compressor 3, and connects the outlet of the compressor 3 to the inlet of the expansion turbine 4 through a first heat exchanger 5 and a second heat exchanger 6.
  • the refrigerant circulating pipe 21 connects the outlet of the expansion turbine 4 to the inlet of the compressor 3 through a brine cooler (heat exchanger) 22 and the second heat exchanger 6.
  • dry air or dry nitrogen is hermetically sealed.
  • the compressor 3 compresses air refrigerant taken into the refrigerant circulating pipe 21 from the atmosphere and supplied thereto, and outputs the compressed air to the first heat exchanger 5.
  • the first heat exchanger 5 is supplied with the atmospheric air by a pump P and carries out heat exchange between the air refrigerant compressed by the compressor 3 and an atmospheric air to cool the compressed air refrigerant.
  • the compressed air refrigerant cooled by the first heat exchanger 5 is supplied to the second heat exchanger 6.
  • the second heat exchanger 6 carries out heat exchange between the air refrigerant cooled by the first heat exchanger 5 and low temperature air refrigerant in the refrigerant circulating pipe 21 outputted from the brine cooler 22.
  • the air refrigerant cooled by the second heat exchanger 6 is supplied to the expansion turbine 4.
  • the expansion turbine 4 adiabatically expands the air refrigerant cooled by the second hear exchanger 6, resulting in the air refrigerant being further cooled to about -80°C.
  • the air refrigerant cooled by the expansion turbine 4 is supplied to the brine cooler 22. Brine circulated in a brine line 23 is cooled in the brine cooler 22 with the air refrigerant cooled by the expansion turbine 4.
  • the cooled brine is circulated in the brine line 23 by a pump P and cools a refrigeration storage 7, in which refrigeration objects are stored.
  • the air refrigerant outputted from the brine cooler 22 is used to carry out the heat exchange in the second heat exchanger 6 and then is supplied to the inlet of the compressor 3.
  • the refrigerant circulating pipe 21 is filled with dry air or dry nitrogen.
  • the dry air or dry nitrogen is taken into the refrigerant circulating pipe 21.
  • the air or nitrogen is dehumidified to the extent that condensation does not occur in the refrigerant circulating pipe 21 even when its temperature becomes lowest.
  • the dry air or dry nitrogen is introduced in the refrigerant circulating pipe 21.
  • the following method is employed as a method of replacing normal air with the dry air or dry nitrogen in the refrigerant circulating line 21.
  • the dry air or the dry nitrogen is introduced from a valve (not shown) provided in a lower pressure portion of the refrigerant circulating pipe 21, for example, in front of the second heat exchanger 6, and is circulated in the refrigerant circulating pipe 21. Then, air mixed with the dry air or dry nitrogen is discharged from a valve (not shown) provided in a higher pressure portion of the refrigerant circulating pipe 21, for example, in front of an inlet of the expansion turbine 4.
  • a hygrometer the above-mentioned procedure is repeatedly carried out until a humidity in the refrigerant circulating pipe 21 reaches a predetermined value at which condensation does not occur in the refrigerant circulating pipe 21 even under the lowest temperature of the air or nitrogen.
  • the refrigeration storage 7 may be any of the following storages:
  • a Coefficient of Performance (COP) in the closed type air refrigerant refrigerator 20 in the first embodiment is shown in the following equation (4).
  • COP Cp ⁇ - 30 - t t Wc - Wt
  • G refrigerant flow rate G necessary for 10 RT is shown by the following equation (5).
  • 38.6 Cp ⁇ - 30 - T t ⁇ G
  • ⁇ G 38.6 Cp ⁇ - 30 - t t kg / s (Cp: specific heat, G: flow rate, k: specific heat ratio, p: density)
  • the refrigeration performance when air containing moisture as the conventional refrigerant is used can be obtained by calculating a quantity of heat required to lower the air temperature from -30 [°C] to -62 [°C] and regarding the quantity of heat as degradation in refrigeration performance.
  • the quantity of heat [per unit refrigerant low rate (1 [kg/s])] required to lower the air temperature from -30 [°C] to -62 [°C] is as follows in each of saturated wet air and the dry air:
  • the closed type air refrigerant refrigerator in the first embodiment invention has a mechanism to prevent refrigerant filled in a refrigerant circulating pipe in the refrigerator from directly contacting atmosphere. Also, dry air or dry nitrogen as the refrigerant is dehumidified to the extent that condensation does not occur in the refrigerant circulating pipe even when its temperature becomes lowest. Thus, it is unnecessary to install a filter for removing frost and ice generated through condensation of moisture contained in the air refrigerant, which occurs during the cooling operation of the air refrigerant in a conventional air refrigerant refrigerator. Thus, manufacturing and maintenance costs of the air refrigerant refrigerator can be reduced.
  • the air refrigerant refrigerator of the first embodiment it is not necessary to stop the operation of the refrigerator because of cleaning of the filter and defrosting. Furthermore, manufacturing and maintenance costs of the air refrigerant refrigerator can be reduced. For these reasons, a continuous cooling operation of refrigeration targets such as specific drugs and living bodies becomes possible, which must be kept under a cooling condition at all times. Furthermore, in the first embodiment, by using the refrigerant containing no moisture, generation of rust in the refrigerator can be prevented and the reliability of the refrigerator itself can be improved.
  • Fig. 4 is a schematic diagram showing the configuration of the closed type air refrigerant refrigerator according to the second embodiment of the present invention.
  • the closed type air refrigerant refrigerator of the second embodiment is different from that of the first embodiment in a cooling method of the refrigeration storage 7.
  • a brine line 24 is used in addition to the brine line 23 in the first embodiment.
  • the brine line 24 is connected to the brine line 23 through shut valves.
  • Fig. 7 is a schematic diagram showing the configuration of the closed type air refrigerant refrigerator 40 according to the third embodiment of the present invention.
  • the basic configuration and operating principle of the closed type air refrigerant refrigerator 40 in the third embodiment are the same as those of the refrigerator in the first embodiment. Therefore, the description thereof is omitted.
  • the brine cooler 22 provided in the first embodiment is not provided. Instead, the refrigerant circulating pipe 21 is directly arranged in the refrigeration storage 7. By circulating the cooled air refrigerant in the refrigerant circulating pipe 21 disposed in the refrigeration storage 7, the temperature in the refrigeration storage 7 is lowered, thereby keeping the refrigeration objects stored in the refrigeration storage 7 cool.
  • a refrigerant is filled in the refrigerant circulating pipe 21 prior to start of the refrigerator 40, as in the first embodiment.
  • the dry air or the dry nitrogen is used as the refrigerant filled in the refrigerant circulating pipe 21.
  • manufacturing and maintenance costs can be further reduced as compared with the first embodiment.
  • the third embodiment as in the first embodiment, it is unnecessary to install a filter for removing frost and ice generated through condensation of moisture contained in the air refrigerant.
  • the operation of the refrigerator is not stopped because of cleaning of the filter and defrosting.
  • a continuous cooling operation of the refrigeration objects such as specific drugs and living bodies becomes possible, which must be kept under cooling condition at all times.
  • manufacturing and maintenance costs of the air refrigerant refrigerator can be reduced. Also, by using the refrigerant containing no moisture, rust can be prevented from occurring in the refrigerator and thus the reliability of the refrigerator itself can be improved.
  • the refrigeration storage 7 may be the objects described in the first embodiment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Devices That Are Associated With Refrigeration Equipment (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP06003379.2A 2005-09-09 2006-02-20 Kühler mit geschlossenem Luftkreislauf und dessen Kühlverfahren Expired - Fee Related EP1762793B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2005261972A JP2007071507A (ja) 2005-09-09 2005-09-09 密閉型空気冷媒冷凍装置

Publications (3)

Publication Number Publication Date
EP1762793A2 true EP1762793A2 (de) 2007-03-14
EP1762793A3 EP1762793A3 (de) 2013-12-25
EP1762793B1 EP1762793B1 (de) 2018-05-30

Family

ID=37591519

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06003379.2A Expired - Fee Related EP1762793B1 (de) 2005-09-09 2006-02-20 Kühler mit geschlossenem Luftkreislauf und dessen Kühlverfahren

Country Status (4)

Country Link
EP (1) EP1762793B1 (de)
JP (1) JP2007071507A (de)
DK (1) DK1762793T3 (de)
NO (1) NO342771B1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103743141A (zh) * 2013-01-11 2014-04-23 摩尔动力(北京)技术股份有限公司 异相传热热力学循环系统

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008129599A1 (ja) * 2007-04-05 2008-10-30 Earthship K.K. 自動除霜機能を備えた空気冷却システム
TWI493144B (zh) * 2012-09-07 2015-07-21 Ind Tech Res Inst 熱交換循環系統
CN105698434A (zh) * 2016-04-13 2016-06-22 桂林电子科技大学 一种压缩空气制冷及制备热水装置

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1440000A (en) * 1920-05-03 1922-12-26 Charles E Bonine Refrigeration
GB557093A (en) * 1942-09-24 1943-11-03 J & E Hall Ltd Improvements in or relating to cooling at low temperatures
US5462110A (en) * 1993-12-30 1995-10-31 Sarver; Donald L. Closed loop air-cycle heating and cooling system
EP0690275A2 (de) * 1994-06-27 1996-01-03 Praxair Technology, Inc. Kühlanlage mit einem geschlossenen Hochdruck-Primärkühlkreislauf und einem Sekundärkühlkreislauf
US5644928A (en) * 1992-10-30 1997-07-08 Kajima Corporation Air refrigerant ice forming equipment
JP2004317081A (ja) * 2003-04-18 2004-11-11 Kobe Steel Ltd 空気冷凍機

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP3390801B2 (ja) * 1995-03-16 2003-03-31 日本酸素株式会社 低温破砕装置における被破砕物の冷却方法
JPH1047829A (ja) * 1996-07-29 1998-02-20 Nippon Sanso Kk 冷凍倉庫における被冷凍物の冷凍方法及び装置

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1440000A (en) * 1920-05-03 1922-12-26 Charles E Bonine Refrigeration
GB557093A (en) * 1942-09-24 1943-11-03 J & E Hall Ltd Improvements in or relating to cooling at low temperatures
US5644928A (en) * 1992-10-30 1997-07-08 Kajima Corporation Air refrigerant ice forming equipment
US5462110A (en) * 1993-12-30 1995-10-31 Sarver; Donald L. Closed loop air-cycle heating and cooling system
EP0690275A2 (de) * 1994-06-27 1996-01-03 Praxair Technology, Inc. Kühlanlage mit einem geschlossenen Hochdruck-Primärkühlkreislauf und einem Sekundärkühlkreislauf
JP2004317081A (ja) * 2003-04-18 2004-11-11 Kobe Steel Ltd 空気冷凍機

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103743141A (zh) * 2013-01-11 2014-04-23 摩尔动力(北京)技术股份有限公司 异相传热热力学循环系统
CN103743141B (zh) * 2013-01-11 2017-03-08 摩尔动力(北京)技术股份有限公司 异相传热热力学循环系统

Also Published As

Publication number Publication date
JP2007071507A (ja) 2007-03-22
NO20060744L (no) 2007-03-12
NO342771B1 (no) 2018-08-06
EP1762793A3 (de) 2013-12-25
EP1762793B1 (de) 2018-05-30
DK1762793T3 (en) 2018-07-02

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