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US3818718A - Heat exchanger for compressed air dryer - Google Patents

Heat exchanger for compressed air dryer Download PDF

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Publication number
US3818718A
US3818718A US00354890A US35489073A US3818718A US 3818718 A US3818718 A US 3818718A US 00354890 A US00354890 A US 00354890A US 35489073 A US35489073 A US 35489073A US 3818718 A US3818718 A US 3818718A
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passageway
wall
air
tank
outlet
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C Freese
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    • 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
    • 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
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
    • F28D7/103—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S165/00—Heat exchange
    • Y10S165/909—Regeneration

Definitions

  • ABSTRACT A heat exchanger for removing moisture from compressed air and other gases in which the precooling, cooling and reheating sections are in telescoped relation.
  • FIG. 1 is a section through a heat exchanger for removing moisture from compressed air and the like
  • FIG. 2 is a section on line 2-2 of FIG. I
  • FIG. 3 is a section through another embodiment.
  • FIG. I there is shown a tank having side walls I and upper and lower headers 2, 3. At the lower end of the side walls are inlet and outlet fittings 4, 5 for connection in a compressed air line.
  • the tank and its fittings are constructed to withstand the air pressure.
  • the tank is shown as of circular cross section but obviously other shapes could be used.
  • Within the tank are heat exchange passageways 6, 7, 8, 9 in telescoping relation to each other.
  • the heat exchange passageway 6, which is outermost, is formed by a wall 10 spaced inward from the inner surface of the wall 1 and extending between an annular lower header 11 and an annular upper header 12.
  • the lower header II is fixed to the side wall I of the tank below the inlet fitting 4 and supports the wall 10 and also closes the lower end of the passageway 6 so that the incoming air is directed upward in the direction of arrow 13.
  • the header l2 at the upper end of the wall 10 directs the flow from the outlet of passageway 6 in the direction of arrow 14 to the inlet end of passageway 9 formed between a wall 15 depending from the header l2 and a conduit 16 for a refrigerant.
  • the refrigerant enters the lower end of conduit 16 as indicated by arrow 17 and flows out the upper end as indicated by arrow 18.
  • the outer surface of the conduit 16 may be provided with spikes or fins 19 or other expedients for increasing the heat exchange surface.
  • Expedients for increasing the heat exchange surface may obviously be used for the other walls forming heat exchange passageways. While flowing through the passageway 9, the air temperature is lowered below its dew point and moisture and other condensibles are condensed, falling into a sump 20 formed by the header 3. Dirt entrained in the air also falls into the sump.
  • a drain fitting 21 is provided to remove excessive liquid accumulation in the sump. Some liquid in the sump is advantageous since this liquid is cooled by the refrigerant in conduit 16 and therefore provides a further heat exchange surface for lowering the dew point of the air and thereby removing moisture.
  • the enlarged space 22 between the outlet 23 of passageway 9 and the inlet 24 of passageway 8 encourages moisture drop out and discourages entrainment of moisture in the air entering the inlet of passageway 8.
  • Passageway 7 is in heat exchange relation to wall 10 of passageway 6 and also to wall 29 of passageway 8.
  • the heat exchange relation to wall 10 serves to precool the incoming air flowing in the direction of arrow, 13.
  • the heat exchange relation to the wall 29 is minimized by making wall 29 of a poor heat conductor. While the inlet air flowing in the direction of arrow 13 is being precooled, the air flowing downward through passageway 7 in the directionof arrow 30 is being reheated. At the lower or outlet end of passageway 7 the header l1 deflects the air to the outlet fitting 5.
  • the walls 10, 15, 29 which form the heat exchanging passageways are all supported by the header 11. These walls may be of thin metal since none of these walls is required to stand the operating pressure of the air. Both headers 11 and 12 also have the function of directing the air flow through the heat exchanger passageways, as described above.
  • the structure has high thermal efficiency because the warm incoming air is at the outside of the tank and the cold or dehydrated air is at the center of the tank. Sharing of walls of the heat exchanger passageways improves the thermal efficiency by direct conduction of heat from the air through the metal walls.
  • Wall 15 is shared by passageways 8, 9.
  • Wall 29 is shared by passageways 7, 8.
  • Wall 10 is shared by passageways 6, 7.
  • the structure also makes efficient use of space due to the sinuous air flow of the heat exchanging surfaces. The structure further simplifies the construction and reduces the space requirements.
  • FIG. 3 there is shown a modification in which the dew point of the air is lowered by chilled liquid spray and in which the inlet and outlet for the compressed air is at the top of the tank rather than at the bottom.
  • the cooling apparatus of FIG. 3 could be substituted in FIG. 1 and vice versa.
  • the tank has upper and lower headers 41, 42 and inlet and outlet fittings 43, 44 for compressed air. These parts are sized to withstand the air pressure.
  • heat exchange passageways 45, 46, 47, 48 in telescoping relation to each other.
  • the passageway is formed by a wall 49 and the inner surface of side wall 40 of the tank.
  • the wall 49 is fixed at its upper end and supported by the header 41 and at its lower end is fixed to an annular header 50 extending between wall 49 and a wall 51 which defines the passageway 48.
  • the compressed air entering inlet 43 is compelled to flow downward through the passageway 45 and enters the lower end of passageway 48 and flows upward as indicated by arrow 52.
  • the air While flowing up through passageway 48, the air is cooled by a refrigerated liquid spray obtained from a liquid chiller 53 and circulated by a pump 54 from a sump 55 in header 42 to a spray head 56 discharging into the upper end of passageway 48.
  • a series of staggered baffles 57 provide an extended gas and liquid contact interface between the compressed air and the chilled liquid. This results in cooling of the compressed air below its dew point so that the moisture is absorbed by the liquid which falls into the sump as indicated by drops 58.
  • the liquid in the sump provides a further heat exchange surface for cooling the air entering the lower end of passageway 48. Excess accumulation of liquid in the sump is prevented by a valve 59.
  • an anti-freeze is required. This is obtained from an injector 60 having a sensing element 61 responding to the freezing temperature of the liquid in the sump which injects anti-freeze through line 62 as required by the sensor.
  • the outlet from the control valve 59 would ordinarily lead to anti-freeze recovery apparatus such as a still.
  • the cooled air leaving the upper or outlet end of the passageway 48 flows downward through passageway 47 formed by wall 51 and a surrounding wall 63 which is supported by the header 41. Air leaving the lower or outlet end of passageway 47 flows upward into the inlet end of passageway 46 formed between the walls 49 and 63. At the outlet end of the passageway 46 the air is deflected by the header 41 into the outlet fitting 44.
  • the incoming compressed air from inlet fitting 43 is precooled by the air in passageway 46. This heat exchange both precools the incoming air and reheats the outgoing air leaving fitting 44. The air is further cooled by contact with the liquid in the sump 55 and by the liquid spray in passage 48.
  • the heat exchange passageways are in telescoping relation, improving the thermal efficiency and decreasing the space requirements and the cost of production. Only the tanks and its headers are sized to withstand the operating pressure. The internal walls are designed for heat transfer and not forpressure.
  • Apparatus for dehumidifying air or other gas comprising a plurality of telescoped passageways each having an inlet at one end and an outlet at the opposite end, a first passageway being outermost with its inlet receiving air to be dehumidified, a second passageway being innermost with its inlet receiving the air from the outlet of the first passageway and conducting such air in the opposite direction to the direction of flow in the first passageway and having therein refrigerating means in heat exchange relation to such air, a third passageway surrounding and in heat exchange relation to the second passageway with its inlet receiving the air from the outlet of the second passageway and conducting such air in the same direction as the direction of flow in the first passageway, and a fourth passageway between and in heat exchange relation to the first passageway with its inlet receiving the air from the outlet of the third passageway and conducting such air in the opposite direction to the direction of flow in the first passageway, the flow being sequentially through the first, second, third and fourth passageways.
  • the apparatus of claim 1 having a tank with inlet and outlet fittings, the first passageway being connected to the inlet fitting and formed between the inner surface of a side wall of the tank and a first wall spaced inward from said surface and the fourth passageway being connected to the outlet fitting and formed between said first wall and a second wall spaced inward from said first wall.
  • the refrigerating means comprises a conduit carrying in said second passageway a refrigerating medium.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Analytical Chemistry (AREA)
  • General Chemical & Material Sciences (AREA)
  • Oil, Petroleum & Natural Gas (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

A heat exchanger for removing moisture from compressed air and other gases in which the precooling, cooling and reheating sections are in telescoped relation.

Description

United States Patent [191 Freese Primary ExaminerWilliam J. Wye Attorney, Agent, or FirmRalph Hammar [57] ABSTRACT A heat exchanger for removing moisture from compressed air and other gases in which the precooling, cooling and reheating sections are in telescoped relation.
16 Claims, 3 Drawing Figures HEAT EXCHANGER FOR COMPRESSED AIR DRYER [76] Inventor: Charles E. Freese, 5140 Woodland,
Forest Park, Ga. 30050 [22] Filed: Apr. 26, 1973 [21] Appl. No.: 354,890
[52] US. Cl. 62/272, 62/90, 62/92, 62/93, 62/317, 62/428 [51] Int. Cl. F25d 21/00 [58] Field of Search 62/90, 93, 92, 428, 272, 62/317 [56] References Cited UNITED STATES PATENTS l,093,869 4/1914 Leinert 62/93 l n 9 a A 1- a A |O-i A 30- A z= A 15- A a, i-E 4 n si PATENTED JUN25 1974 1 HEAT EXCHANGER FOR COMPRESSED DRYER This invention is intended to increase the efficiency and reduce the cost of manufacture and operation of heat exchangers for removing moisture from air or other gases. In a preferred form, the heat exchanger is shown for removing moisture from compressed air but other uses are obviously possible.
In the drawing, FIG. 1 is a section through a heat exchanger for removing moisture from compressed air and the like, FIG. 2 is a section on line 2-2 of FIG. I, and FIG. 3 is a section through another embodiment.
In FIG. I there is shown a tank having side walls I and upper and lower headers 2, 3. At the lower end of the side walls are inlet and outlet fittings 4, 5 for connection in a compressed air line. The tank and its fittings are constructed to withstand the air pressure. The tank is shown as of circular cross section but obviously other shapes could be used. Within the tank are heat exchange passageways 6, 7, 8, 9 in telescoping relation to each other. The heat exchange passageway 6, which is outermost, is formed by a wall 10 spaced inward from the inner surface of the wall 1 and extending between an annular lower header 11 and an annular upper header 12. The lower header II is fixed to the side wall I of the tank below the inlet fitting 4 and supports the wall 10 and also closes the lower end of the passageway 6 so that the incoming air is directed upward in the direction of arrow 13. The header l2 at the upper end of the wall 10 directs the flow from the outlet of passageway 6 in the direction of arrow 14 to the inlet end of passageway 9 formed between a wall 15 depending from the header l2 and a conduit 16 for a refrigerant. The refrigerant enters the lower end of conduit 16 as indicated by arrow 17 and flows out the upper end as indicated by arrow 18. The outer surface of the conduit 16 may be provided with spikes or fins 19 or other expedients for increasing the heat exchange surface. Expedients for increasing the heat exchange surface may obviously be used for the other walls forming heat exchange passageways. While flowing through the passageway 9, the air temperature is lowered below its dew point and moisture and other condensibles are condensed, falling into a sump 20 formed by the header 3. Dirt entrained in the air also falls into the sump. A drain fitting 21 is provided to remove excessive liquid accumulation in the sump. Some liquid in the sump is advantageous since this liquid is cooled by the refrigerant in conduit 16 and therefore provides a further heat exchange surface for lowering the dew point of the air and thereby removing moisture. The enlarged space 22 between the outlet 23 of passageway 9 and the inlet 24 of passageway 8 encourages moisture drop out and discourages entrainment of moisture in the air entering the inlet of passageway 8.
The air entering the lower end of passageway 8 flows upward as indicated by arrow 25 and at its upper or outlet end 26 is deflected downward by header 12 into the inlet end 27 of passageway 7 as indicated by arrow 28. Passageway 7 is in heat exchange relation to wall 10 of passageway 6 and also to wall 29 of passageway 8. The heat exchange relation to wall 10 serves to precool the incoming air flowing in the direction of arrow, 13. The heat exchange relation to the wall 29 is minimized by making wall 29 of a poor heat conductor. While the inlet air flowing in the direction of arrow 13 is being precooled, the air flowing downward through passageway 7 in the directionof arrow 30 is being reheated. At the lower or outlet end of passageway 7 the header l1 deflects the air to the outlet fitting 5.
The walls 10, 15, 29 which form the heat exchanging passageways are all supported by the header 11. These walls may be of thin metal since none of these walls is required to stand the operating pressure of the air. Both headers 11 and 12 also have the function of directing the air flow through the heat exchanger passageways, as described above. The structure has high thermal efficiency because the warm incoming air is at the outside of the tank and the cold or dehydrated air is at the center of the tank. Sharing of walls of the heat exchanger passageways improves the thermal efficiency by direct conduction of heat from the air through the metal walls. Wall 15 is shared by passageways 8, 9. Wall 29 is shared by passageways 7, 8. Wall 10 is shared by passageways 6, 7. The structure also makes efficient use of space due to the sinuous air flow of the heat exchanging surfaces. The structure further simplifies the construction and reduces the space requirements.
In FIG. 3 there is shown a modification in which the dew point of the air is lowered by chilled liquid spray and in which the inlet and outlet for the compressed air is at the top of the tank rather than at the bottom. Obviously the cooling apparatus of FIG. 3 could be substituted in FIG. 1 and vice versa.
In the structure of FIG. 3, the tank has upper and lower headers 41, 42 and inlet and outlet fittings 43, 44 for compressed air. These parts are sized to withstand the air pressure. Within the tank are heat exchange passageways 45, 46, 47, 48 in telescoping relation to each other. The passageway is formed by a wall 49 and the inner surface of side wall 40 of the tank. The wall 49 is fixed at its upper end and supported by the header 41 and at its lower end is fixed to an annular header 50 extending between wall 49 and a wall 51 which defines the passageway 48. The compressed air entering inlet 43 is compelled to flow downward through the passageway 45 and enters the lower end of passageway 48 and flows upward as indicated by arrow 52. While flowing up through passageway 48, the air is cooled by a refrigerated liquid spray obtained from a liquid chiller 53 and circulated by a pump 54 from a sump 55 in header 42 to a spray head 56 discharging into the upper end of passageway 48. A series of staggered baffles 57 provide an extended gas and liquid contact interface between the compressed air and the chilled liquid. This results in cooling of the compressed air below its dew point so that the moisture is absorbed by the liquid which falls into the sump as indicated by drops 58. The liquid in the sump provides a further heat exchange surface for cooling the air entering the lower end of passageway 48. Excess accumulation of liquid in the sump is prevented by a valve 59. If the liquid is chilled below the freezing point of the moisture, an anti-freeze is required. This is obtained from an injector 60 having a sensing element 61 responding to the freezing temperature of the liquid in the sump which injects anti-freeze through line 62 as required by the sensor. When the injector is used, the outlet from the control valve 59 would ordinarily lead to anti-freeze recovery apparatus such as a still.
The cooled air leaving the upper or outlet end of the passageway 48 flows downward through passageway 47 formed by wall 51 and a surrounding wall 63 which is supported by the header 41. Air leaving the lower or outlet end of passageway 47 flows upward into the inlet end of passageway 46 formed between the walls 49 and 63. At the outlet end of the passageway 46 the air is deflected by the header 41 into the outlet fitting 44.
In the operation, the incoming compressed air from inlet fitting 43 is precooled by the air in passageway 46. This heat exchange both precools the incoming air and reheats the outgoing air leaving fitting 44. The air is further cooled by contact with the liquid in the sump 55 and by the liquid spray in passage 48.
In both forms of the invention, the heat exchange passageways are in telescoping relation, improving the thermal efficiency and decreasing the space requirements and the cost of production. Only the tanks and its headers are sized to withstand the operating pressure. The internal walls are designed for heat transfer and not forpressure.
What is claimed is:
1. Apparatus for dehumidifying air or other gas comprising a plurality of telescoped passageways each having an inlet at one end and an outlet at the opposite end, a first passageway being outermost with its inlet receiving air to be dehumidified, a second passageway being innermost with its inlet receiving the air from the outlet of the first passageway and conducting such air in the opposite direction to the direction of flow in the first passageway and having therein refrigerating means in heat exchange relation to such air, a third passageway surrounding and in heat exchange relation to the second passageway with its inlet receiving the air from the outlet of the second passageway and conducting such air in the same direction as the direction of flow in the first passageway, and a fourth passageway between and in heat exchange relation to the first passageway with its inlet receiving the air from the outlet of the third passageway and conducting such air in the opposite direction to the direction of flow in the first passageway, the flow being sequentially through the first, second, third and fourth passageways.
2. The apparatus of claim 1 in which the third passageway shares a wall with the second passageway and also shares a wall with the fourth passageway.
3. The apparatus of claim 1 in which the fourth passageway shares a wall with the first passageway.
4. The apparatus of claim 1 having a tank with inlet and outlet fittings, the first passageway being connected to the inlet fitting and formed between the inner surface of a side wall of the tank and a first wall spaced inward from said surface and the fourth passageway being connected to the outlet fitting and formed between said first wall and a second wall spaced inward from said first wall.
5. The apparatus of claim 4 in which a third wall forms the second passageway and is spaced inward from the second wall to form the third passageway.
6. The apparatus of claim 5 in which the tank has upper and lower headers and the lower header provides a sump below said second and third walls.
7. The apparatus of claim 6 in which the sump is refrigerated to provide a further cooling surface.
8. The apparatus of claim 1 in which the refrigerating means comprises a chilled liquid spray.
9. The apparatus of claim 1 in which the refrigerating means comprises a conduit carrying in said second passageway a refrigerating medium.
10. The apparatus of claim 8 in which the chilled liquid is a solution with a freezing point below the normal freezing point of water.
11. The apparatus of claim 4 in which the first and second walls are supported by a header fixed to the tank.
12. The apparatus of claim 5 in which the third wall is supported by said header.
13. The apparatus of claim 5 in which the tank has upper and lower headers and the lower header provides a sump below said third wall.
14. The apparatus of claim 5 in which the tank has upper and lower headers and the lower header provides a sump below said first, second and third walls.
15. The apparatus of claim 13 in which the sump is refrigerated to provide a further cooling surface.
16. The apparatus of claim 14 in which the sump is refrigerated to provide a further cooling surface.

Claims (16)

1. Apparatus for dehumidifying air or other gas comprising a plurality of telescoped passageways each having an inlet at one end and an outlet at the opposite end, a first passageway being outermost with its inlet receiving air to be dehumidified, a second passageway being innermost with its inlet receiving the air from the outlet of the first passageway and conducting such air in the opposite direction to the direction of flow in the first passageway and having therein refrigerating means in heat exchange relation to such air, a third passageway surrounding and in heat exchange relation to the second passageway with its inlet receiving the air from the outlet of the second passageway and conducting such air in the same direction as the direction of flow in the first passageway, and a fourth passageway between and in heat exchange relation to the first passageway with its inlet receiving the air from the outlet of the third passageway and conducting such air in the opposite direction to the direction of flow in the first passageway, the flow being sequentially through the first, second, third and fourth passageways.
2. The apparatus of claim 1 in which the third passageway shares a wall with the second passageway and also shares a wall with the fourth passageway.
3. The apparatus of claim 1 in which the fourth passageway shares a wall with the first passageway.
4. The apparatus of claim 1 having a tank with inlet and outlet fittings, the first passageway being connected to the inlet fitting and formed between the inner surface of a side wall of the tank and a first wall spaced inward from said surface and the fourth passageway being connected to the outlet fitting and formed between said first wall and a second wall spaced inward from said first wall.
5. The apparatus of claim 4 in which a third wall forms the second passageway and is spaced inward from the second wall to form the third passageway.
6. The apparatus of claim 5 in which the tank has upper and lower headers and the lower header provides a sump below said second and third walls.
7. The apparatus of claim 6 in which the sump is refrigerated to provide a further cooling surface.
8. The apparatus of claim 1 in which the refrigerating means comprises a chilled liquid spray.
9. The apparatus of claim 1 in which the refrigerating means comprises a conduit carrying in said second passageway a refrigerating medium.
10. The apparatus of claim 8 in which the chilled liquid is a solution with a freezing point below the normal freezing point of water.
11. The apparatus of claim 4 in which the first and second walls are supported by a header fixed to the tank.
12. The apparatus of claim 5 in which the third wall is supported by said header.
13. The apparatus of claim 5 in which the tank has upper and lower headers and the lower header provides a sump below said third wall.
14. The apparatus of claim 5 in which the tank has upper and lower headers and the lower header provides a sump below said first, second and third walls.
15. The apparatus of claim 13 in which the sump is refrigerated to provide a further cooling surface.
16. The apparatus of claim 14 in which the sump is refrigerated to provide a further cooling surface.
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Cited By (24)

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FR2372649A1 (en) * 1976-12-03 1978-06-30 Willot Henri AIR NEUTRALIZATION AND CLEANING UNIT
US4193443A (en) * 1977-11-28 1980-03-18 Orion Machinery Co., Ltd. Heat exchanger for cooling system compressed air dehumidifiers
US4249391A (en) * 1979-09-19 1981-02-10 Thomas Mackey Cooling tower vapor recovery unit
FR2505999A1 (en) * 1981-05-12 1982-11-19 White Jeffrey METHOD AND APPARATUS FOR CONDENSING STEAM TO CONTINUOUSLY EXTRACT CONDENSATE FROM COMPRESSED GAS CURRENT
US4471836A (en) * 1982-01-15 1984-09-18 Arthur C. Knox, Jr. Vent condenser
US4565794A (en) * 1983-12-16 1986-01-21 John Stephens Production of silica gel and an adsorbent, absorbent product from sericitic clay
US4646819A (en) * 1985-08-09 1987-03-03 Monsanto Company Apparatus for drying air
US4726826A (en) * 1987-07-17 1988-02-23 The M. W. Kellogg Company Method for partial condensation of hydrocarbon gas mixtures
US4726817A (en) * 1985-01-23 1988-02-23 Rippert Roger Method and device for recovering in liquid form the water present in the atmosphere in vapor form
US4749030A (en) * 1987-09-28 1988-06-07 Knox Jr Arthur C Device for condensing organic solvents
US4854129A (en) * 1987-06-11 1989-08-08 Hickley Pieter Cooling process and apparatus
US4918935A (en) * 1989-03-13 1990-04-24 Trent Warren C Fluidic flow control
EP0405613A1 (en) * 1989-06-30 1991-01-02 Mta S.R.L Heat exchanger
US5020334A (en) * 1990-02-23 1991-06-04 Gas Research Institute Localized air dehumidification system
US5230166A (en) * 1992-07-21 1993-07-27 Deng Gwo Jen Air drier
US5327740A (en) * 1991-11-18 1994-07-12 Ckd Corporation Dehumidifier
US5611209A (en) * 1994-11-30 1997-03-18 Ckd Corporation Dehumidifier
US5644925A (en) * 1996-07-02 1997-07-08 Chaves; Manuel J. Air conditioning system condensing trap
US5715696A (en) * 1993-07-26 1998-02-10 Hiross International Corporation B.V. Arrangement for reducing the humidity content of a gaseous medium
WO2000071223A1 (en) * 1999-05-20 2000-11-30 Alfa Laval Ab A device for treating a gas
US20070079624A1 (en) * 2005-10-07 2007-04-12 Marine Desalination Systems, L.L.C. Atmospheric moisture harvesters
US9482453B2 (en) 2010-01-15 2016-11-01 Ingersoll-Rand Company Air dryer assembly
WO2020125008A1 (en) * 2018-12-20 2020-06-25 佛山市天地元一净化设备有限公司 Heat exchange structure for compressed air refrigerated dryer
US11680391B2 (en) * 2018-01-25 2023-06-20 Northwestern University Surfaces with high surface areas for enhanced condensation and airborne liquid droplet collection

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US2740268A (en) * 1953-05-14 1956-04-03 Calvin M Jones High speed air conditioner circulating chamber
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US2209661A (en) * 1937-11-20 1940-07-30 Superheater Co Ltd Cooling, drying, and reheating compressed air
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US4200442A (en) * 1976-12-03 1980-04-29 Centre De Recherche Fondamentale "Rivieren" S.P.R.L. Apparatus for neutralizing and purifying air
FR2372649A1 (en) * 1976-12-03 1978-06-30 Willot Henri AIR NEUTRALIZATION AND CLEANING UNIT
US4193443A (en) * 1977-11-28 1980-03-18 Orion Machinery Co., Ltd. Heat exchanger for cooling system compressed air dehumidifiers
US4249391A (en) * 1979-09-19 1981-02-10 Thomas Mackey Cooling tower vapor recovery unit
FR2505999A1 (en) * 1981-05-12 1982-11-19 White Jeffrey METHOD AND APPARATUS FOR CONDENSING STEAM TO CONTINUOUSLY EXTRACT CONDENSATE FROM COMPRESSED GAS CURRENT
US4410035A (en) * 1981-05-12 1983-10-18 White Jeffrey A Condensing apparatus and method for pressurized gas
US4471836A (en) * 1982-01-15 1984-09-18 Arthur C. Knox, Jr. Vent condenser
US4565794A (en) * 1983-12-16 1986-01-21 John Stephens Production of silica gel and an adsorbent, absorbent product from sericitic clay
US4726817A (en) * 1985-01-23 1988-02-23 Rippert Roger Method and device for recovering in liquid form the water present in the atmosphere in vapor form
US4646819A (en) * 1985-08-09 1987-03-03 Monsanto Company Apparatus for drying air
AU597495B2 (en) * 1987-06-11 1990-05-31 Cornelius Johannes Claassen Cooling process and apparatus
US4854129A (en) * 1987-06-11 1989-08-08 Hickley Pieter Cooling process and apparatus
US4726826A (en) * 1987-07-17 1988-02-23 The M. W. Kellogg Company Method for partial condensation of hydrocarbon gas mixtures
US4749030A (en) * 1987-09-28 1988-06-07 Knox Jr Arthur C Device for condensing organic solvents
US4918935A (en) * 1989-03-13 1990-04-24 Trent Warren C Fluidic flow control
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US5020334A (en) * 1990-02-23 1991-06-04 Gas Research Institute Localized air dehumidification system
US5327740A (en) * 1991-11-18 1994-07-12 Ckd Corporation Dehumidifier
US5230166A (en) * 1992-07-21 1993-07-27 Deng Gwo Jen Air drier
US5715696A (en) * 1993-07-26 1998-02-10 Hiross International Corporation B.V. Arrangement for reducing the humidity content of a gaseous medium
US5611209A (en) * 1994-11-30 1997-03-18 Ckd Corporation Dehumidifier
US5644925A (en) * 1996-07-02 1997-07-08 Chaves; Manuel J. Air conditioning system condensing trap
WO2000071223A1 (en) * 1999-05-20 2000-11-30 Alfa Laval Ab A device for treating a gas
US6536511B1 (en) 1999-05-20 2003-03-25 Alfa Laval Ab Device for treating a gas
US20070079624A1 (en) * 2005-10-07 2007-04-12 Marine Desalination Systems, L.L.C. Atmospheric moisture harvesters
US7293420B2 (en) * 2005-10-07 2007-11-13 Marine Desalination Systems, L.L.C. Atmospheric moisture harvesters
US9482453B2 (en) 2010-01-15 2016-11-01 Ingersoll-Rand Company Air dryer assembly
US11680391B2 (en) * 2018-01-25 2023-06-20 Northwestern University Surfaces with high surface areas for enhanced condensation and airborne liquid droplet collection
WO2020125008A1 (en) * 2018-12-20 2020-06-25 佛山市天地元一净化设备有限公司 Heat exchange structure for compressed air refrigerated dryer

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