US3861165A - Dehumidification of air - Google Patents

Dehumidification of air Download PDF

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Publication number
US3861165A
US3861165A US402670A US40267073A US3861165A US 3861165 A US3861165 A US 3861165A US 402670 A US402670 A US 402670A US 40267073 A US40267073 A US 40267073A US 3861165 A US3861165 A US 3861165A
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coolant
primary
heat exchanger
air
primary coolant
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US402670A
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Itsuro Hirano
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D20/00—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00
    • F28D20/02—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat
    • F28D20/021—Heat storage plants or apparatus in general; Regenerative heat-exchange apparatus not covered by groups F28D17/00 or F28D19/00 using latent heat the latent heat storage material and the heat-exchanging means being enclosed in one container
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01D—SEPARATION
    • B01D53/00—Separation of gases or vapours; Recovering vapours of volatile solvents from gases; Chemical or biological purification of waste gases, e.g. engine exhaust gases, smoke, fumes, flue gases, aerosols
    • B01D53/26—Drying gases or vapours
    • B01D53/265—Drying gases or vapours by refrigeration (condensation)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
    • F24F2003/144—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0038—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for drying or dehumidifying gases or vapours
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E60/00—Enabling technologies; Technologies with a potential or indirect contribution to GHG emissions mitigation
    • Y02E60/14—Thermal energy storage

Definitions

  • Air may be dehumidified in an apparatus, comprising, [30] Forelgn Apphcatlo Pnomy Data in combination, a primary heat exchanger provided Oct. 2, 1972 Japan 47-97985 with a variable volume primary coolant for environmental cooling for thereby dehumidifying air in pro- [52] US.
  • Suitable primary coolants include admixtures of a suitable liquid, for instance wa- [56] References Cited ter, or an aqueous solution of a freezing point depres- UNITED STATES PATENTS sant, and ice Volume variations of the primary cool- 2,000,467 5/1935 Lindseth 165/26 am Occur as ice in the admixture melts and quid 2,720,084 10/1955 Hailey freezes and accumulates as 3,050,954 8 1962 R0 se. 3,105,362 10/1963 Goiild 62/126 12 Glam, 2 D'awmg F'gures DEHUMIDIFICATION OF AIR BACKGROUND OF THE INVENTION.
  • a suitable liquid for instance wa- [56] References Cited ter, or an aqueous solution of a freezing point depres- UNITED STATES PATENTS sant
  • This invention relates to a method and apparatus for dehumidifying air for the drying thereof.
  • air may be dehumidified in an apparatus, comprising, in combination, a primary heat exchanger provided with a variable volume primary coolant for environmental cooling for thereby dehumidifying air in process, a secondary heat exchanger provided with a circulating secondary coolant for cooling the primary coolant, and means for controlling the circulation of the secondary coolant according to volume variations of the primary coolant.
  • Suitable primary coolants include admixtures ofa suitable liquid, for instance water, or an aqueous solution of a freezing point depressant, and ice. Volume variations of the primary coolant occur as ice in the admixture melts and liquid freezes and accumulates as ice.
  • This invention utilizes heat capacity of the primary coolant for latent heat at its freezing point.
  • the volume thereof must increase during freezing, and the temperature thereof must remain constant during freezing. Any fluid or admixture with these properties may be employed herein as the primary coolant.
  • water or aqueous solutions of selected freezing point depressants such as NaCl or CaCl may be satisfactorily employed as the primary coolant for this invention.
  • Volume variations of the primary coolant, caused by cyclical freezing and melting of parts thereof, are directly utilized for selectively compressing an expansible member, for instance a bellows, for selectively actuating electric circuits for pumping the secondary coolant,
  • volume variations of the primary coolant are utilized directly or through an intermediary gas, for instance air and preferably nitrogen, confined with the primary coolant in a closed-vessel.
  • a pressure switch for controlling the flow of the secondary coolant is driven by pressure variations corresponding to volume variations of the primary coolant or intermediary gas for maintaining the-quantity of the ice admixed with primary coolant between selectively prescribed'maximum and minimum levels correspondingto preselectedupper and lower pressure switch limits.
  • the invention accordingly comprises the several steps and the relationof one or more of such steps with respect to each of the others, and the apparatus embodying features ofconstruction, combinations of ele ments and arrangement of parts which are adapted to effect such steps, all exemplified in the following detailed disclosure, and the scope of the invention will be indicated in the claims.
  • FIG. 1 is a schematic representation of one type of apparatus for dehumidification of air-constructed in accordance with the invention.
  • FIG. 2 is a schematic representation of another type of apparatus, also constructed in accordance with this invention.
  • an adiabatic, pressure resisting closed vessel 10 is filled with a primary coolant, comprising water or a suitable aqueous solution of freezing point depressant, admixed with a small quantity of a suitable gas, such as air and preferably N
  • a suitable gas such as air and preferably N
  • a coiled pipe 11 is arranged interiorly of vessel I0 for forming a primary heat exchanger, and first and second portions thereof extend exteriorly for providing an inlet 12 and an outlet 13 therefor. On outlet 13, a drain valve 14 is mounted.
  • Another coiled pipe 15 is also arranged interiorly of vessel 10 for forming a secondary heat exchanger, and a portion thereof extends exteriorly of vessel 10 for connecting the pipe I5 to a source of a secondary coolant, such as a refrigerator (not shown).
  • a source of a secondary coolant such as a refrigerator (not shown).
  • the adiabatic, pressure resisting wall of the vessel I0 has an expansible member 16, such as bellows, which responds to volume variations of the primary coolant and an end thereof I7 is displaceable according to volume variations. Displaceable end 17 may be displaced along electrical contacts 18, I9 and 20.
  • Three circuits including the three contacts 18, I9 and 20 and also three lamps 21, 22 and 23, are, respectively, adapted to be energized by a source 24.
  • the lamp 21 is a yellow lamp, which lights when there is an overload.
  • the lamp 22 is a blue lamp, which lights when the refrigerator opcrates and secondary coolant circulates, for operating the secondary heat exchanger.
  • the lamp 23 is a red lamp, which lights when the refrigerator is not operating and secondary coolant is not flowing, but the secondary heat exchanger is still in operation.
  • an electric motor 26 is energized by another power source 27 for driving a pump 31 which pumps secondary coolant through coiled pipe 15 of the secondary heat exchanger.
  • an electromagnetic switch 25 is actuated for deenergizing the motor 26 and, in turn, the pump 31 for automatically avoiding excessive cooling.
  • the primary coolant confined inside the closed vessel 10 is continuously agitated by a stirrer 28 driven by a motor 33 for maintaining the primary coolant at a substantially uniform temperature.
  • the primary coolant has been cooled to C. or near 0 C., and mixed with ice.
  • Air to be dried which may be compressed air, is admitted into the coiled pipe 11 of the primary heat exchanger through inlet 12 for cooling to near 0 C., by the primary coolant, and for separation from water suspended therein.
  • outlet 13 and condensate is drawn off through the drain valve 14.
  • the primary coolant is confined within adiabatic, pressure resisting closed vessel either with or without a small quantity of air which when present accumulates inside the expansible member 16 for transmitting volume variations of the primary coolant to displaceable end 17 thereof and volume variations of the primary coolant are transmitted directly or through the intermediate air to displaceable end 17 which responds accordingly.
  • Mounted on the top wall of closed vessel 10 are a pressure relief means 29 and a pressure gauge 30, for adjusting the maximum pressure of the primary coolant.
  • the relief means 29 and the pressure gauge 30 may be of a conventional construction well-known to the art-skilled.
  • the temperature of the inlet air for processing is higher than 0 C., and therefore the temperature of the primary coolant tends to be elevated at the primary heat exchanger. Because the primary coolant is mixed with ice, it has a substantial heat capacity and a substantial resistance to temperature elevations. While the secondary coolant circulates, the quantity of ice in the primary coolant increases and the overall volume of the primary coolant increases for thereby displacing end 17 of expansible member 16 from its connection with contact 18 to contact with contact 19. Thus, yellow lamp 21 goes out and blue lamp 22 ignites. This indicates that, at this instant, dehumidification of the input air is ready to be effected and started with the primary coolant, and is the desirable normal condition.
  • the primary coolant includes about percent of ice at this instant.
  • yellow lamp 21 ignites while the secondary heat exchanger is operating at full capacity, that signifies that the dehumidifying capacity of the apparatus is short, and therefore, it is necessary to reduce air input.
  • This condition may occur when the volume ratio of ice to primary coolant is less than 20 percent, whereby the reduced volume of primary coolant deflates expansible member 16 and end 17 thereof contacts with contact 18 of yellow lamp 21.
  • the primary coolant to be confined within adiabatic, pressure resisting closed vessel 10 may be water or a selected aqueous solution of a freezing point depressant. Suitable freezing point depressants include sodium salts such as NaCl, calcium salts such as CaCl and the like.
  • the freezing point of the primary coolant may be adjusted from 0 C. to lO C., by the freezing point depressant. When the adjustment is made and when the temperature of the output air at outlet 13 is near 0 C., the temperature gradient between the interior of the coiled pipe 11 and the primary coolant within the closed vessel 10 steepens. By virtue thereof, the heat transferring surface may be reduced for economizing the construction cost of the apparatus.
  • FIG. 2 illustrates another embodiment of the invention.
  • Air for drying is admitted through inlet 12 into a water separator 48 and is cooled thereby.
  • the cooled air is admitted into a heat exchanger 49, wherein the cooled input air is further cooled by the output air directed to the outlet 13.
  • the twice pre-cooled air is then admitted into an air chamber 47 provided with a coiled pipe 45 interiorly arranged therein constituting the primary heat exchanger and the precooled air is substantially cooled and dehumidified by this primary heat exchanger.
  • Condensate drainage occurs counterflow to the air in process for further cooling the latter and condensate is collected in water separator 48 which is provided with a drain valve 14 for expelling the condensate out of the apparatus.
  • the primary coolant is water in this embodiment and it is circulated through coiled pipe 45 for forming the primary heat exchanger, and introduced into an adiabatic, pressure resisting closed vessel 41.
  • coiled pipe 45 is connected with the closed vessel 41 by connecting pipes 43 and 46, and the connecting pipe 43 is provided with a pump 44.
  • Adiabatic, pressure resisting closed vessel 41 is provided thereon with a pressure resisting air vessel 42 provided with a pressure relief means 29 and a pressure gauge 30.
  • a coiled pipe 15 for recirculating the secondary coolant from the refrigerator (not shown), which thereby constitutes the secondary heat exchanger inside the closed vessel 4].
  • the secondary coolant is a Freon gas.
  • a control switch 35 is also connected on pressure resisting air vessel 42 and controls the flow of the recirculating secondary coolant in response to the air pressure in the pressure resisting air vessel 42 or volume variations of the primary coolant, for maintaining the volume of ice contained in the primary coolant between about 20 percent and 50 percent.
  • the control switch 35 it is preferred to use a pressure having an upper and lower limit, which may be set in such a manner that the limits correspond to the maximum and the minimum pressures for maintaining the volume of ice within the above-mentioned range.
  • An apparatus for dehumidifying air comprising, in combination, a primary heat exchanger for dehumidifying air, a primary coolant for cooling said primary heat exchanger, a secondary heat exchanger for cooling said primary coolant, a secondary coolant for cooling said secondary heat exchanger, means for controlling circulation of said secondary coolant through said secondary heat exchanger responsive to volume variations of said primary coolant, an adiabatic, pressure resisting closed vessel for housing said primary heat exchanger, said primary heat exchanger including an air chamber for circulating air in process, a heat exchanging element being arranged in said air chamber for recirculating said primary coolant, and means for recirculating said primary coolant through said heat exchanging element; and another heat exchanger arranged in said air chamber for precooling air to be treated with treated air.
  • said primary coolant comprises an admixture of water or an aqueous solution of a freezing point depressant, and ice.
  • said primary heat exchanger comprises a heat exchanger having air inlet and outlet portions for circulating air for processing there through and including an adiabatic, pressure resisting closed vessel, said vessel housing said primary coolant, said heat exchanger being mounted in said vessel with said inlet and outlet portions extending exteriorly thereof.
  • said means for controlling circulation of said secondary coolant comprises an expansible member connected to said vessel, said expansible member being responsive to volume variations of said primary coolant caused by cyclically freezing and melting a portion thereof and including a circuit actuable by said expansible member for interrupting circulating of said secondary coolant through said another heat exchanger.
  • said secondary heat exchanger comprises an adiabatic, pressure resisting closed chamber, means for circulating said primary coolant through said chamber for cooling said primary coolant and a heat exchanging element arranged in said chamber for carrying circulating secondary coolant for cooling said chamber, said secondary coolant being recirculated through said heat exchanging element and including a refrigerant source for cooling said secondary coolant.
  • controlling means comprises a pressure switch having an upper and lower limit adapted for, respectively, representing maximum and minimum optimal ice contents for said primary coolant, for controlling secondary coolant recirculation for thereby maintaining ice content between said optimal maximum and minimum limits.
  • claim 1 including a water separator for collecting condensate extracted from air in process, said water separator being arranged below said another heat exchanger, and means for connecting said water separator and said air chamber for carrying condensate therefrom to said water separator.
  • a method for dehumidfying air comprising cooling said air with a primary coolant, confining said primary coolant within a sealed pressure vessel, circulating said primary coolant through a primary heat exchanger, cooling said primary coolant with a secondary coolant, selectively recirculating said secondary coolant through a secondary heat exchanger and a refrigerant source, and controlling said recirculation of said secondary coolant according to control responses transmitted at predetermined primary coolant volume variation levels for maintaining an ice volume in said primary coolant of between 20 and 50 percent; said primary coolant being an admixture of water or an aqueous solution of a freezing point depressant, and ice.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • Analytical Chemistry (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Combustion & Propulsion (AREA)
  • Drying Of Gases (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
US402670A 1972-10-02 1973-10-02 Dehumidification of air Expired - Lifetime US3861165A (en)

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Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2307237A1 (fr) * 1975-04-10 1976-11-05 Conditionair Appareil echangeur-refroidisseur pour fluides gazeux
US4235081A (en) * 1978-10-31 1980-11-25 Kellogg-American, Inc. Compressed air dryer
EP0067044A2 (en) * 1981-06-05 1982-12-15 Russell Finex Limited Heat exchanger
US4829778A (en) * 1987-09-23 1989-05-16 Via Gmbh Measuring gas cooling device
US4950316A (en) * 1989-07-28 1990-08-21 Charles Harris Dehumidification system
EP0308531B1 (de) * 1987-09-23 1990-12-27 VIA Gesellschaft für Verfahrenstechnik mbH Messgaskühleinrichtung
US5327740A (en) * 1991-11-18 1994-07-12 Ckd Corporation Dehumidifier
WO1995025935A2 (en) * 1994-03-24 1995-09-28 Turbo X Air cooling system with recirculating condensate
US5553459A (en) * 1994-07-26 1996-09-10 The Watermarker Corp. Water recovery device for reclaiming and refiltering atmospheric water
US5564277A (en) * 1990-10-01 1996-10-15 General Cryogenics Incorporated Dehumidifier for cryogenic refrigeration system
US5715696A (en) * 1993-07-26 1998-02-10 Hiross International Corporation B.V. Arrangement for reducing the humidity content of a gaseous medium
EP1081445A2 (en) * 1999-08-31 2001-03-07 O.M.I. Srl Drying plant for compressed air
WO2001017665A1 (de) * 1999-09-09 2001-03-15 Kta Kalte- Und Drucklufttechnische Anlagen Gmbh Druckluftkältetrockner
US20040206095A1 (en) * 2002-12-24 2004-10-21 Kaeser Kompressoren Gmbh Low-temperature dryer
US20090014161A1 (en) * 2005-11-28 2009-01-15 Volvo Lastvagnar Ab Container arrangement
CN105536449A (zh) * 2015-12-15 2016-05-04 新凤鸣集团湖州中石科技有限公司 间冷式压缩空气冷却干燥装置
US9638367B2 (en) * 2012-10-26 2017-05-02 Mitsubishi Heavy Industries, Ltd. Saturator and natural gas reforming system provided with same

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2000467A (en) * 1931-09-09 1935-05-07 Lindseth Theodore Cooling, freezing and heating apparatus
US2720084A (en) * 1953-06-09 1955-10-11 James G Hailey Energy storage for air conditioning systems
US3050954A (en) * 1960-05-06 1962-08-28 Edwin H Royse Moisture condenser
US3105362A (en) * 1962-03-05 1963-10-01 Gen Motors Corp Refrigerating apparatus with indicating means

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2000467A (en) * 1931-09-09 1935-05-07 Lindseth Theodore Cooling, freezing and heating apparatus
US2720084A (en) * 1953-06-09 1955-10-11 James G Hailey Energy storage for air conditioning systems
US3050954A (en) * 1960-05-06 1962-08-28 Edwin H Royse Moisture condenser
US3105362A (en) * 1962-03-05 1963-10-01 Gen Motors Corp Refrigerating apparatus with indicating means

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2307237A1 (fr) * 1975-04-10 1976-11-05 Conditionair Appareil echangeur-refroidisseur pour fluides gazeux
US4235081A (en) * 1978-10-31 1980-11-25 Kellogg-American, Inc. Compressed air dryer
EP0067044A2 (en) * 1981-06-05 1982-12-15 Russell Finex Limited Heat exchanger
EP0067044A3 (en) * 1981-06-05 1983-05-11 Russell Finex Limited Heat exchanger
US4829778A (en) * 1987-09-23 1989-05-16 Via Gmbh Measuring gas cooling device
EP0308531B1 (de) * 1987-09-23 1990-12-27 VIA Gesellschaft für Verfahrenstechnik mbH Messgaskühleinrichtung
US4950316A (en) * 1989-07-28 1990-08-21 Charles Harris Dehumidification system
US5564277A (en) * 1990-10-01 1996-10-15 General Cryogenics Incorporated Dehumidifier for cryogenic refrigeration system
US5327740A (en) * 1991-11-18 1994-07-12 Ckd Corporation Dehumidifier
US5715696A (en) * 1993-07-26 1998-02-10 Hiross International Corporation B.V. Arrangement for reducing the humidity content of a gaseous medium
WO1995025935A2 (en) * 1994-03-24 1995-09-28 Turbo X Air cooling system with recirculating condensate
WO1995025935A3 (en) * 1994-03-24 1995-11-09 Turbo X Air cooling system with recirculating condensate
US5553459A (en) * 1994-07-26 1996-09-10 The Watermarker Corp. Water recovery device for reclaiming and refiltering atmospheric water
EP1081445A2 (en) * 1999-08-31 2001-03-07 O.M.I. Srl Drying plant for compressed air
EP1081445A3 (en) * 1999-08-31 2001-11-14 O.M.I. Srl Drying plant for compressed air
WO2001017665A1 (de) * 1999-09-09 2001-03-15 Kta Kalte- Und Drucklufttechnische Anlagen Gmbh Druckluftkältetrockner
US20040206095A1 (en) * 2002-12-24 2004-10-21 Kaeser Kompressoren Gmbh Low-temperature dryer
EP1434023A3 (de) * 2002-12-24 2005-08-03 Kaeser Kompressoren GmbH Kältetrockner
US7040100B2 (en) 2002-12-24 2006-05-09 Kaeser Kompressoren Gmbh Low-temperature dryer
US20090014161A1 (en) * 2005-11-28 2009-01-15 Volvo Lastvagnar Ab Container arrangement
US9638367B2 (en) * 2012-10-26 2017-05-02 Mitsubishi Heavy Industries, Ltd. Saturator and natural gas reforming system provided with same
CN105536449A (zh) * 2015-12-15 2016-05-04 新凤鸣集团湖州中石科技有限公司 间冷式压缩空气冷却干燥装置

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