US3750415A - Method and apparatus for drying a gas and chilling it to low temperatures - Google Patents

Method and apparatus for drying a gas and chilling it to low temperatures Download PDF

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Publication number
US3750415A
US3750415A US00230752A US3750415DA US3750415A US 3750415 A US3750415 A US 3750415A US 00230752 A US00230752 A US 00230752A US 3750415D A US3750415D A US 3750415DA US 3750415 A US3750415 A US 3750415A
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United States
Prior art keywords
heat exchanger
gas
refrigerant
hot
flow
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Expired - Lifetime
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US00230752A
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English (en)
Inventor
W Peuchen
G Pase
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WILSTAN Corp
GC Industries Inc
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PEUCHEN Inc
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Assigned to GC INDUSTRIES, INC. reassignment GC INDUSTRIES, INC. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: PEUCHEN, WILFRED S.
Assigned to WILSTAN CORPORATION reassignment WILSTAN CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: PEUCHEN, WILFREDS SR.
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/16—Filtration; Moisture separation
    • 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)
    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21F—PAPER-MAKING MACHINES; METHODS OF PRODUCING PAPER THEREON
    • D21F1/00—Wet end of machines for making continuous webs of paper
    • D21F1/02—Head boxes of Fourdrinier machines
    • D—TEXTILES; PAPER
    • D21—PAPER-MAKING; PRODUCTION OF CELLULOSE
    • D21F—PAPER-MAKING MACHINES; METHODS OF PRODUCING PAPER THEREON
    • D21F1/00—Wet end of machines for making continuous webs of paper
    • D21F1/54—Skimming devices, e.g. froth ledges
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting

Definitions

  • ABSTRACT A method and apparatus are provided for continuously drying and chilling a high temperature, pressurized gas such as air to sub-zero temperatures.
  • the high temperature pressurized gas is passed alternately through each of two parallel heat exchangers containing cooling coils through which cold refrigerant from a refrigeration system is passed. While one of the heat exchangers is being cooled by the cold refrigerant, the hot, pressurized gas is passed through it in heat exchange relationship with the cooling coils. Simultaneously, the other heat exchanger is cleared of moisture and other condensables by passing hot refrigerant gas from the compressor of the refrigeration system through its cooling coils.
  • the flow of hot refrigerant gas to the one being defrosted is terminated and replaced with the flow of cold refrigerant to cool it in order to prevent carryover of moisture on changing stages of operation.
  • a continuous flow of cooled, dried pressurized gas is obtained from the two heat exchangers and can be passed through a third heat exchanger provided with refrigerated coils to further chill the gas to sub-zero temperature.
  • the cooled gas from thetwo parallel heat exchangers can be cycled through a preliminary heat exchanger to effect pre-cooling of the entering hot, pressurized gas.
  • This invention relates to an improved method and apparatus for chilling and removing moisture from a hot, pressurized gas such as air by directing the gas through heat exchangers containing cold refrigeration coils, whereby condensed moisture is periodically removed from the heat exchangers without interrupting the continuous function of the system and without requiring the utilization of additional energy supplied from sources external to the apparatus.
  • the present invention is directed to an improved method for providing a continuous flow of chilled, dried, pressurized gas by passing a stream of hot, pressurized gas through one of a pair of heat exchangers containing cooling coils which are chilled by refrigerant from a refrigeration system containing compressor and condenser means. Simultaneously with the passage of refrigerant through the first of the pair of heat exchangers to effect cooling and removal of condensables, the second of the pair of heat exchangers is cleared of condensed moisture by directing through its cooling coils aflow of hot refrigerant gas directly from the compressor of the refrigeration system.
  • transition stages are employed whereby, prior to switching the flow of pressurized gas from one heat exchanger to the other, the flow of hot refrigerant gas from the compressor into the heat exchanger being defrosted is terminated, and a flow of cold refrigerant from the refrigeration system is directed into its coils while, at the same time, pressurized gas continues to be passed over the chilled coils of the other heat exchanger.
  • Another object of this invention is to provide a method and apparatus for chilling and drying pressurized gas whereby a continuous cyclic system is employed which permits chilling and drying of the compressed gas and removal of condensables without any carryover of condensables into the chilled, dry, pressurized gas.
  • FIGS. 1, 2 and 3 are block schematic diagrams which depict the cyclic operationof the present invention.
  • FIG. 4 is a semi-schematic drawing with interior views showing the complete heat exchanger and refrigeration system of the present invention for cooling and drying pressurized air.
  • FIGS. 1, 2, and 3 For an understanding of the four-stage operation of the invention.
  • High temperature, pressurized gas is supplied to the system by the externally located compressor 51.
  • high temperature, pressurized gas is passed through the heat exchanger A where moisture and other condensables are condensed out of the gas by means of refrigeration coils (not shown) cooled by refrigerant supplied by the compresset 52, and the condenser 54.
  • Hot, compressed refrigerant gas from the compressor 52, which is not directed to the condenser 54 is simultaneously passed into the refrigeration coils (not shown) of the heat exchanger B to melt ice and other condensables deposited when the heat exchanger is in the stage of operation in which it cools the high temperature, pressurized gas.
  • Both hot and cold refrigerant are returned from the refrigeration coils of the heat exchangers, A and B, to the compressor 52 by conduits which are not shown.
  • the pressurizedgas leaves the heat exchanger and is introduced into the heat exchanger C, which contains refrigeration coils (not shown) maintained at very low temperature (i.e., below F.) by means of refrigerant from the compressor 53 and condenser 55.
  • the dry, pressurized gas which is cooled to a temperature of 60 F. emerges from the heat exchanger C in a continuous flow.
  • Refrigerant from the refrigeration coils in the heat exchanger C is returned to the compressor 53 by means of a suitable conduit, not shown.
  • the heat exchanger B which is being defrosted by hot refrigerant gas from the compressor 52, is by-passed by the flow of pressurized gas through the system.
  • the functions of the heat exchangers, A and B are exactly reversed from those of the first stage.
  • hot, pressurized gas from the compressor 51 is introduced into the heat exchanger B where it is cooled and condensables removed by refrigeration coils cooled by refrigerant supplied from the condenser 54.
  • the heat exchanger A is excluded from the flow of pressurized gas and is cleared of frozen condensables by means of hot refrigerant gas from the compressor 54.
  • the stream of chilled, pressurized gas emerges from the heat exchanger B and through the heat exchanger C, maintained at sub-zero temperature, from where it continues to emerge in a continuous flow at a temperature of -60 F.
  • stage 4 The fourth, and final, stage of operation is not shown in FIGS. 1, 2, and 3, but consists of a transitional precooling as in stage 2, before returning to stage 1.
  • stage 4 the flow of pressurized gas is continued through the heat exchangers, B and C, as in stage 3. Defrosting of the heat exchanger A is discontinued, however, by terminating the flow of hot refrigerant gas from the compressor 52. Instead, the heat exchanger A is pre-cooled by directing the flow of refrigerant from the condenser 54 into the refrigerant coils of A. In this stage, the cooling of the pressurized gas in the heat exchanger B is continued by also directing the flow of refrigerant from the condenser 54 into its refrigeration coils.
  • dual cylindrical, parallel heat exchangers are shown at l and 1A with coils for carrying cold refrigerant shown within the cylindrical heat exchanger columns at 36 and 37, respectively.
  • An additional heat exchanger consisting of 6 parallel, horizontal, interconnected cylinders, is shown at 3.
  • Compressor 4 provides hot, pressurized gas through the pipe 25 into the condenser 6.
  • Suitable liquid coolant is supplied to the coils 41 within the condenser 6 and through the orifice 44 and removed through 43. This liquid coolant is cycled from a source not shown.
  • Cold refrigerant liquid is passed from the condenser 6 through pipe 27 to the solenoid valves 10 and 12 which control the flow of cold refrigerant liquid, respectively, through the thermostatic expansion valves 16 and 17.
  • pipe 26 provides for the direct passage of hot, pressurized refrigerant gas from the compressor 4 to the solenoid valves 11 and 13.
  • Cold refrigerant, after passing through the refrigeration coils 36 and 37, is removed as gas from the top of the heat exchangers l and 1A, respectively, by means of pipe 28 which returns the refrigerant to the compressor 4.
  • Compressor 5 provides hot, compressed refrigerant gas through the pipe 29 to the condenser 7 where it is condensed into cold refrigerant liquid by a suitable coolant passing through the orifice 46 to the cooling pipes 42 and back out through 45 where it is recycled and chilled by suitable circulating and cooling mechanisms not shown.
  • Cold refrigerant liquid passes from the condenser 7 through the pipe 31 to the solenoid control valve 14 and the thermostatic expansion valve 18, enters the heat exchanger 3 and is carried through the heat exchanger coils 38.
  • the cold refrigerant is finally returned by means of the pipe 32 as gas to the compressor 5.
  • Pipe 30 provides for direct passage of hot, compressed refrigerant gas to the solenoid valve 15 and then into the heat exchanger pipe 38 for cycling through the heat exchanger coils 38 and return by pipe 32 to the compressor 5.
  • Valve means are provided at 19 for admitting into the system hot, pressurized air which is to be chilled and dried.
  • An optional pre-cooling cylinder isshown at 2 and provided with cooling coils 40.
  • a pipe passes from the top of the pre-cooler 2 and divides into the separate pipes, 20 and 21, which enter the bottom of the heat exchangers l and 1A. Additional pipes exit, respectively, at the top of each of the heat exchangers l and 1A and are each provided with the solenoid valves 8 and 9, respectively.
  • the pipes emerging from the top sides of the heat exchangers A and IA merge into pipe 22 which returns to the bottom of the pre-eooler where it is connected into the cooling coil 40.
  • Pipe 23 is connected at the exit end of the cooling coil 40 and conducts chilled air to horizontal heat exchanger 3.
  • Pipe 24 provides for emergence of the cooled, dry, pressurized air from the heat exchanger 3 and leads to the exit valve 39. Drains provided with valves are shown at 33 for the heat exchanger 1, at 34 for the heat exchanger 1A and at 35 for the heat exchanger 3.
  • high temperature, pressurized air is admitted from a source not shown through the valve 19 optionally into the pre-cooler 2 where it is chilled by the cold air from heat exchanger 1 or IA, depending upon which of the solenoid valves, 8 and 9, are open or closed, circulating through the coil 40.
  • the pre-cooled, pressurized air then emerges from the top of the precooler and alternately flows either through pipe 20 into heat exchanger 1 or pipe 21 into heat exchanger 1A, depending upon which of the solenoid valves, 8 and 9, are opened or closed.
  • a continuous flow of cold, chilled air is, however, maintained from either the heat exchanger 1 or 1A through the pipe 22 where it is optionally used to pre-cool fresh, incoming, high temperature, pressurized air in the pre-cooler 40 and then is passed through the pipe 23 to the heat exchanger 3.
  • the pre-cooler 40 is dispensed with and the flow of chilled air from the heat exchanger 1 and 1A is directed immediately to the heat exchanger 3.
  • Cold refrigerant is provided to the heat exchangers l and 1A from the compressor 4 and the condenser 6 by means of pipes 25 and 27.
  • cold refrigerant liquid passes through the expansion valve 16 to the heat exchanger coils 36 in the heat exchanger 1.
  • the solenoid valve 10 is closed and solenoid 12 open to provide the flow of cold refrigerant liquid through the expansion valve 17 to the coil 37 in the heat exchanger 1A.
  • Cold refrigerant gas emerges from the respective cooling coils of the heat exchangers 1 and 1A and is passed through the common tubing 28 back to the compressor 4.
  • the refrigeration coils, 36 and 37, in the heat exchangers l and 1A through which cold refrigerant passes, provide the primary chilling of the high temperature air which is passed through the heat exchanger and also for the removal of condensables such as water vapor from the air.
  • These condensables are subsequently removed from the heat exchangers without interruption of the flow of air through the system by passing hot refrigerant gas directly from the compressor 4 through the pipe 26 into the respective pairs of cooling coils, 36 and 37. Control of this flow of hot refrigerant gas to cause defrosting of the coils is effected by means of the solenoid valves, 11 and 13.
  • both the solenoid 12 leading to the heat exchanger 1A and the solenoid 10 leading to the heat exchanger 1 are opened while both solenoids 11 and 13 are closed, thereby excluding the flow of hot, refrigerant gas from either heat exchanger 1 or 1A, while permitting the refrigeration coils 36 and 37 to be cooled simultaneously by the flow of cold refrigerant from the condenser 6 through the expansion valves 16 and 17.
  • the solenoid valve 8 is closed and solenoid valve 9 opened, thereby causing the flow of pressurized air from the pre-cooler 2 to be directed through pipe 21 into heat exchanger 1A.
  • solenoid valve 10 is closed to exclude cold refrigerant from the cooling coils of heat exchanger 1.
  • Solenoid valve 13 remains closed while 11 is opened so that hot refrigerant gas from the compressor 4 defrosts the coils 36 of heat exchanger 1 in the same manner that heat exchanger 1A was previously cleared of condensates removed from the hot, pressurized air.
  • Cooling is effected in the heat exchanger 3 by means of the interconnected coils 38 through which passes cold refrigerant from the condenser 7. While removal of condensables such as water vapor from the heat exchanger 3 is not frequently. required, due to its having been previously eliminated from the air stream in the heat exchangers l and 1A, occasionally the solenoid valve 14 is closed and solenoid valve 15 opened so that, rather than cold refrigerant from the condenser, hot refrigerant gas from the compressor 5 is directed into the coils 38 to free them of accumulated frozen moisture.
  • Activation of the various solenoid valves used to control the flow of gases and liquids is accomplished by means of conventional electrical circuits and relays which have not been shown. These circuits can involve largely manual control of the solenoids or can be extensively automated to respond to timed signals for changing cycles, for example.
  • the expansion valves shown at 1 6, 17, and 18 in H6. 4 meter the amount of liquid refrigerant entering the respective heat exchangers to maintain the predetermined temperature and pressure of the refrigerant gas.
  • These valves are conventionally activated by means of sensors (not shown) which measure the temperature and pressure of the refrigerant gas after it has absorbed heat from the gas being cooled.
  • the refrigeration components of the present invention including the compressors, condensers, expansion valves and refrigerant are, in themselves, conventional in design and operation.
  • An apparatus for continuously cooling and drying a pressurized gas comprising in combination first and second heat exchanger means adapted for cooling and condensing moisture from said pressurized gas; a third heat exchanger means adapted for further cooling and condensing moisture from the gas cooled and dried in said first and second heat exchangers; first and second refrigeration means operatively connected with and each adapted to provide, in a cyclic system, to said first and second heat exchangers and to said third heat exchanger, respectively, separate flows of hot, pressurized refrigerant gas and cold refrigerant and to receive a return flow of cold refrigerant gas from said heat exchangers; said first and second heat exchanger means being operatively disposed in parallel and each provided with operatively connected means for regulating and circulating alternating flows of hot refrigerant gas and cold refrigerant from said first refrigeration means through itself and returning the gas to the refrigeration means; said third heat exchanger means also being provided with means for regulating and circulating alternate flows of hot refrigerant gas and cold refriger
  • the apparatus of claim 1 which further comprises preliminary heat exchanger means provided with means operatively connected with said first and second heat exchangers for circulating the flow of cooled, high pressurized gas from said first and second heat exchangers through itself and then to said third heat exchanger means; said preliminary heat exchanger means being further provided with operatively disposed means for passing the stream of high temperature, pressurized gas from its source in heat exchange relationship with said cooled gas and then to said first and second heat exchanger means.
  • said refrigeration means comprises in combination condenser means and compressor means operatively connected to provide a flow of hot, compressed refrigerant gas to said condenser means and alternately gas from said compressor through the cooling coils of the second of said heat exchangers to melt substances previously condensed from the high pressure gas;
  • the apparatus of claim 1 which is operatively connected to provide cold, pressurized air to a device for blow-molding plastic articles.
  • a four-stage continuous process for cooling hot, high pressure gas comprising the steps of:
  • Claim 3 s The apparatus of claim 1 wherein saidrefrigeration means comprises in combination condenser means and compressor means operatively connected to provide a flow of hot, compressed refrigerant gas to said condenser means and alternately to each of said first and second heat exchangers; said condenser means being further adapted to receive said hot, compressed refrigerant from said compressor means and to condense and cool it to a refrigerant liquid; means operatively connected to said condenser for regulating and circulating said refrigerant liquid to each of said first and second heat exchangers.
  • Claim 7 A four-stage continuous process for cooling hot,
  • high pressure gas comprising the steps of:

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Thermal Sciences (AREA)
  • Analytical Chemistry (AREA)
  • General Chemical & Material Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Defrosting Systems (AREA)
  • Moulds For Moulding Plastics Or The Like (AREA)
  • Blow-Moulding Or Thermoforming Of Plastics Or The Like (AREA)
  • Drying Of Solid Materials (AREA)
US00230752A 1972-03-01 1972-03-01 Method and apparatus for drying a gas and chilling it to low temperatures Expired - Lifetime US3750415A (en)

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US23075272A 1972-03-01 1972-03-01

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US (1) US3750415A (fr)
JP (1) JPS5333777B2 (fr)
CA (1) CA987118A (fr)
DE (1) DE2310068A1 (fr)
FR (1) FR2174137B1 (fr)
GB (1) GB1418345A (fr)
IT (1) IT977526B (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4055965A (en) * 1976-09-08 1977-11-01 Society Messier Heat pump installation
US4157649A (en) * 1978-03-24 1979-06-12 Carrier Corporation Multiple compressor heat pump with coordinated defrost
US4744224A (en) * 1987-07-27 1988-05-17 Erickson Donald C Intermittent solar ammonia absorption cycle refrigerator
US5108475A (en) * 1991-01-28 1992-04-28 Venturedyne, Ltd. Solvent recovery system with means for reducing input energy
WO2000071223A1 (fr) * 1999-05-20 2000-11-30 Alfa Laval Ab Dispositif permettant de traiter un gaz
US20060107669A1 (en) * 2004-11-05 2006-05-25 Radisch Ingo K Modular refrigerated dryer apparatus and method
US20100083676A1 (en) * 2008-10-02 2010-04-08 Island Sky Corporation Water production system and method with ozone recharge
US20160178249A1 (en) * 2014-12-18 2016-06-23 Lg Electronics Inc. Outdoor device for an air conditioner
CN112121605A (zh) * 2020-09-28 2020-12-25 安徽文质信息科技有限公司 一种工业气体干燥用复合式冷热循环干燥装置

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
SE431615B (sv) * 1981-07-16 1984-02-20 Munters Ab Carl Anordning for avfuktning av ett medium
AT400529B (de) * 1994-04-05 1996-01-25 Schwarz Robert Dipl Ing Verfahren und anlage zur trocknung von gasen
DE102012110072A1 (de) * 2012-10-22 2014-04-24 Krones Ag Blasformmaschine mit Reinraum und Trocknungseinrichtung für Luftzuführung
CN112957882B (zh) * 2021-02-03 2022-05-17 厦门艾欣特医用设备有限公司 医用空气冷干机

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2867988A (en) * 1955-10-14 1959-01-13 Paul H Brandt Air dryer construction and method of operation
US2903861A (en) * 1957-09-23 1959-09-15 Felix L Alcus System and apparatus for drying air
US2960840A (en) * 1956-02-27 1960-11-22 Fred J Hosken Method and apparatus for defrosting a refrigeration system
CA642948A (en) * 1962-06-12 The General Supply Company Of Canada Limited Air drying method and apparatus
US3499295A (en) * 1968-06-17 1970-03-10 Emhart Corp Refrigeration system
US3500497A (en) * 1968-01-02 1970-03-17 Phillips Petroleum Co Blow molding apparatus with cooling means
US3572052A (en) * 1969-05-15 1971-03-23 Streater Ind Inc Ducted refrigeration unit

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA642948A (en) * 1962-06-12 The General Supply Company Of Canada Limited Air drying method and apparatus
US2867988A (en) * 1955-10-14 1959-01-13 Paul H Brandt Air dryer construction and method of operation
US2960840A (en) * 1956-02-27 1960-11-22 Fred J Hosken Method and apparatus for defrosting a refrigeration system
US2903861A (en) * 1957-09-23 1959-09-15 Felix L Alcus System and apparatus for drying air
US3500497A (en) * 1968-01-02 1970-03-17 Phillips Petroleum Co Blow molding apparatus with cooling means
US3499295A (en) * 1968-06-17 1970-03-10 Emhart Corp Refrigeration system
US3572052A (en) * 1969-05-15 1971-03-23 Streater Ind Inc Ducted refrigeration unit

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4055965A (en) * 1976-09-08 1977-11-01 Society Messier Heat pump installation
US4157649A (en) * 1978-03-24 1979-06-12 Carrier Corporation Multiple compressor heat pump with coordinated defrost
US4744224A (en) * 1987-07-27 1988-05-17 Erickson Donald C Intermittent solar ammonia absorption cycle refrigerator
US5108475A (en) * 1991-01-28 1992-04-28 Venturedyne, Ltd. Solvent recovery system with means for reducing input energy
WO2000071223A1 (fr) * 1999-05-20 2000-11-30 Alfa Laval Ab Dispositif permettant de traiter un gaz
US6536511B1 (en) 1999-05-20 2003-03-25 Alfa Laval Ab Device for treating a gas
US20060107669A1 (en) * 2004-11-05 2006-05-25 Radisch Ingo K Modular refrigerated dryer apparatus and method
US7793508B2 (en) * 2004-11-05 2010-09-14 Flair Corporation Modular refrigerated dryer apparatus and method
US20100083676A1 (en) * 2008-10-02 2010-04-08 Island Sky Corporation Water production system and method with ozone recharge
US20100083675A1 (en) * 2008-10-02 2010-04-08 Island Sky Corporation Water production system and method with auxiliary refrigeration cycle
US20160178249A1 (en) * 2014-12-18 2016-06-23 Lg Electronics Inc. Outdoor device for an air conditioner
US10156387B2 (en) * 2014-12-18 2018-12-18 Lg Electronics Inc. Outdoor device for an air conditioner
CN112121605A (zh) * 2020-09-28 2020-12-25 安徽文质信息科技有限公司 一种工业气体干燥用复合式冷热循环干燥装置

Also Published As

Publication number Publication date
JPS48100738A (fr) 1973-12-19
JPS5333777B2 (fr) 1978-09-16
FR2174137A1 (fr) 1973-10-12
IT977526B (it) 1974-09-20
FR2174137B1 (fr) 1975-08-22
CA987118A (en) 1976-04-13
GB1418345A (en) 1975-12-17
DE2310068A1 (de) 1973-09-13

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AS Assignment

Owner name: GC INDUSTRIES, INC., P.O. 2810, CITY OF WILMINGTON

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:PEUCHEN, WILFRED S.;REEL/FRAME:003854/0871

Effective date: 19810507

AS Assignment

Owner name: WILSTAN CORPORATION, 800 DELAWARE AVE., SUITE 508,

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:PEUCHEN, WILFREDS SR.;REEL/FRAME:003958/0078

Effective date: 19820324