US3782451A - Hydraulic flow distribution system for multiple pass air cooled heat exchanger - Google Patents

Hydraulic flow distribution system for multiple pass air cooled heat exchanger Download PDF

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Publication number
US3782451A
US3782451A US00264150A US3782451DA US3782451A US 3782451 A US3782451 A US 3782451A US 00264150 A US00264150 A US 00264150A US 3782451D A US3782451D A US 3782451DA US 3782451 A US3782451 A US 3782451A
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fluid
heat exchanger
header
sections
set forth
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R Cates
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MC ACQUISITION Corp
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Marley Co LLC
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F25/00—Component parts of trickle coolers
    • F28F25/02—Component parts of trickle coolers for distributing, circulating, and accumulating liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28C—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA COME INTO DIRECT CONTACT WITHOUT CHEMICAL INTERACTION
    • F28C1/00—Direct-contact trickle coolers, e.g. cooling towers
    • F28C1/04—Direct-contact trickle coolers, e.g. cooling towers with cross-current only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28C—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA COME INTO DIRECT CONTACT WITHOUT CHEMICAL INTERACTION
    • F28C1/00—Direct-contact trickle coolers, e.g. cooling towers
    • F28C1/14—Direct-contact trickle coolers, e.g. cooling towers comprising also a non-direct contact heat exchange
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating
    • 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
    • Y10S261/00—Gas and liquid contact apparatus
    • Y10S261/11—Cooling towers
    • 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
    • Y10S261/00—Gas and liquid contact apparatus
    • Y10S261/77—Plume abatement
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/3149—Back flow prevention by vacuum breaking [e.g., anti-siphon devices]
    • Y10T137/3185—Air vent in liquid flow line

Definitions

  • ABSTRACT A multiple pass heat exchanger for cooling a fluid and having upright fluid conveying structure including sep arate, intercommunicating heat exchanger tube sections for upward and downward flow of fluid relative to a cooling medium such as air and wherein a fluid supply header is joined to the lower end of one of the sections, an overflow weir box is provided at the lower end of the other section with the weir box having an overflow opening while the header has an inlet opening, a fluid supply line is joined to the header inlet and has a valve controlled by-pass line extending therefrom and the weir box and header both have drain orifices therein of smaller size than the overflow opening and inlet respectively, yet larger in diameter than the inlets of the heat exchanger tubes whereby upon interruption of the normal supply of fluid to the sections through said supply line, automatic draining of the sections occurs without the use of mechanical or electrical controls. Similarly, automatic filling of the sections may be accomplished, and if desired any proportion of the fluid to be cooled may be by-passed around the sections.
  • This invention relates to heat exchange structure especially useful for cooling a fluid, as for example water, by bringing the hot liquid into thermal interchange relationship with a cooling medium such as air and wherein a unique filling and draining system is incorporated into the apparatus for providing automatic venting, draining and filling of the exchanger without the necessity of employing mechanical or electrical controls for start-up, normal operation, or shut-down.
  • a stack for inducing natural draft flow of air through the dry heat exchanger and the evaporative cooling section comprises one form of structure for drawing adequate quantities of cooling air across the dry and wet heat exchange sections, or motor driven fan means may be used with equal utility depending upon the type of tower required for a particular job specification and the amount of liquid which must be handled per unit of time.
  • a further object of the invention is to provide hydraulic flow-segregation apparatus as described which embodies a common vent manifold connecting the topmost point of parallel exchangers which are piped in a siphon loop of a piping system for the purpose of preventing the untimely initiation of siphon flow in individual exchangers.
  • the system permits siphon establishment only after the liquid to be cooled is made available to the top most portions of all individual exchangers.
  • a still further important object of the invention is to provide hydraulic flow-segregation apparatus for a heat exchanger which is especially applicable to multiple pass heat exchangers but may be used on single pass exchangers as well, without clogging of the exchanger tubes occurring by virtue of accumlation of solid foreign materials in the tubes, and also may be properly sized for use in any type of cooling tower regardless of the capacity thereof or the means employed to effect flow of cooling air across the tube sections.
  • a still further important object of the invention is to provide a hydraulic flow-segregation system for a heat exchanger which is adapted to bring the fluid to be cooled into indirect thermal interchange relationship with a cooling medium wherein the flow controls may be calibrated during initial start-up with manually positionable valves whereby the system may be started and stoppedv periodically as necessary or desired with freeze-up of the heat exchanger under cold operation conditions being avoided by virtue of automatic draining of the heat exchange tubes upon interruption of supply of fluid thereto.
  • a further important object of the invention is to provide a hydraulic flow-segregation system for controlling flow of fluid through a heat exchanger of the indirect thermal interchange type which is not only useable with single as well as multiple pass tubes, but also particularly useful in the case where it is desired that at least a part of the liquid supply be by-passed around the heat exchanger for the purpose of accommodating less water flow through the dry sections than through the wet section to maintain a minimum head loss to the pumping system while providing adequate flow to the dry heat exchangers.
  • the system is also useable for various applications regardless of the direction of water supply relative to the heat exchange tube sections for maximum space saving and equipment orientation convenience.
  • FIG. I is an essentially schematic representation of an induced draft water cooling tower of the type having a dry cooling section as well as an evaporative segment and illustrating hydraulic flow-segregation apparatus for the dry exchanger section which provides automatic venting, draining and filling of liquid under the control of manually positionable valves.
  • FIG. 2 is a fragmentary, enlarged, vertical crosssectional view of the schematic showing of FIG. 1 and more specifically illustrating the multiple pass heat exchanger structure, inboard hot water supply means and the components for effecting automatic venting, draining and filling of liquid responsive to operation or discontinuance of the fluid supply pump;
  • FIG. 3 is a schematic, fragmentary, enlarged crosssectional view of multiple pass heat exchange structure incorporating automatic venting, draining and filling of liquid similar to the structure of FIG. 2, but illustrating the way in which the liquid to be cooled may be supplied to the heat exchanger outboard from the side thereof illustrated in FIG. 2;
  • FIG. 4 is also an enlarged, schematic, fragmentary vertical cross-sectional view of hydraulic flowsegregation apparatus similar to that previously described but in this case having a single flow path for the liquid relative to the air flow (noting in this respect that the upright supply riser is illustrated as being out of the plane of the heat exchange tubes for clarity, but it is to be understood that in most instances, the upright supply riser is to be located between adjacent upright tube sections of the heat exchanger);
  • FIG. 5 is a fragmentary, enlarged, schematic, generally vertical cross-sectional view of the exchanger apparatus illustrated in FIG. 2 and showing the way in which start up of the heat exchanger may be accomplished in a manner such that the sections are all filled with liquid while starving of adjacent exchangers is avoided;
  • FIG. 6 is a schematic, fragmentary, enlarged vertical cross-sectional view of the same structure illustrated in FIG. 5 but showing the way in which automatic draining of the heat exchanger tubes occurs upon interruption of supply of liquid to the apparatus.
  • the cooling tower 10 shown in schematic form in FIG. 1 of the drawings has been illustrated as being of the induced draft type having a motor driven fan 12 for pulling ambient air through opposed inlet louver faces 14 of the tower casing for passage through the dry and wet sections 16 and 18 thereof respectively.
  • the mixture 0f we. and dry heated air is ultimately discharged through the air velocity increasing stack 19.
  • the novel concepts of this invention are equally applicable to a natural draft tower which usually has a hyperbolic stack located with the dry and wet sections 16 and 18 around the perimeter of the base of the stack.
  • the mechanical draft tower 10illustrated in FIG. 1 has been shown therein only for purposes of simplification and is not to be deemed a limitation of the scope of this invention.
  • the wet section 18 of tower 10 is of generally conventional construction and operation.
  • the open topped hot water distribution basin 20 each have a series of orifices therein for delivering individual streams of hot water from basin 20 onto the upper horizontal face of a corresponding fill assembly 22. Air drawn into the interior of the casing of tower 10 through each inlet face is brought into cross flow relationship with water gravitating from a respective basin 20 into the cold water collection basin 24 underlying the fill assemblies 22.
  • Hot water to be cooled (typically water from the condensing coils of an electrical power generating plant or the like) is furnished via supply line 26 leading to risers 28 in turn connected to respective horizontal manifolds 29.
  • Header feed lines 31 extend from corresponding manifolds 29 across hot water distribution basins 20. Since the air cooled heat exchanger structures 30 are intended as being of essentially identical construction, only one of the same will be described in detail.
  • the multiple pass dry heat exchanger 30 includes a number of upright, finned heat exchange tubes 32 which extend from hot water header 34 to the reverse-flow manifold header 36 communicating with tubes 32 at the uppermost ends thereof.
  • a plurality of other finned heat exchange tubes 37 extend downwardly from header 36 and terminate within the interior of weir box 38.
  • weir box 38 is open at the top thereof presenting an overflow opening 40 therein and has a drain orifice 42 in the bottom thereof.
  • header 34 has a drain orifice 44 and it is important to note that drain 44 is of greater size than the inlets 54 of upright tubes 32. As a consequence, solid materials which cannot flow through the tubes 32 are collected in header 44 and ultimately discharge therefrom via orifice 44 into the hot water collection basin 20 therebelow automatically.
  • vent line 46 intercommunicating all of the reverse flow manifold headers 36 through the medium of vent pipes 48 joining a respective header 36 to the interior of vent line 46.
  • a valve 50 Interposed in each line 48 between vent line 46 and a header 36 is a valve 50 so that one or more of the reverse flow manifold headers 36 may be selectively disconnected from the liquid circuit.
  • Horizontal header feed lines 31 are joined to respective inlets 52 of hot water headers 34 and it is to be seen that each inlet 52 is of greater size than drain orifices 44 although the latter are larger than the inlet openings 54 of each of the upright finned tubes 32.
  • the actual dimensions of the pipes, orifices and weir passages logically are constructed to meet specific applications in accordance with the total water flow rate.
  • the inlet pipe 31 could be about 8 in. 1D. thus causing inlet 52 to be of the same size.
  • Orifice 44 would then be about 2 in., the inlet openings of tubes 54 would be approximately 0.9 to l in., and the overflow opening 40 would be about 3 in. vertical height and 12 ft. long as defined by the upright weir plate which terminates 4 in. above the floor plane in which orifice 42 is located.
  • a by-pass drain line 56 connected to each horizontal feed line 31 is located to drain into the upwardly opening hot water distribution basin therebelow and as schematically illustrated in FIG. 2, a manually positionable valve 58 is located in each by-pass drain line 56 for controlling gravitation of hot water from line 31 into basin 20.
  • hot water supplied via line 26, riser 28, horizontal manifold 29 and feed line 31 flows into header 34 and thence upwardly through finned tubes 32 into reverse flow manifold header 36 (FIG. 5).
  • a portion of the hot water by-passes header 34 via line 56 depending upon the setting of control valve 58 while another proportion of the water gravitates into hot water distribution basin 20 through the drain orifice 44.
  • Water collected in header 36 flows downwardly through tubes 37 into weir box 38 until the water overflows the upper edge thereof defining overflow opening 40.
  • the vent line 46 joining all of the reverse flow manifold headers 36 provides ventilation air from downstream parallel exchangers to prevent a premature partial siphon effect, thereby permitting proper and simultaneous siphon initiation during filling of the tubes 32 and 37 so that there is no tendency for the heat exchanger structures 36 to be devoid of hot water which could present a starved condition in the heat exchangers which are the most remote from the water supply line.
  • Water flowing downwardly in the tubes 37 from header 36 recovers the siphon head so that continuous supply of hot water via lines 26, 28, 29 and 31 forces the liquid to flow uninterruptedly through the structure 30 along an upward path defined by finned tubes 32 and thence downwardly through finned tubes 37.
  • the cooling air normally flows along a path 62 as indicated so that the coolest air first encounters the coldest liquid for most efficient cooling.
  • the valve 58 should empirically be set at a position which permits proper start-up flow rates in the heat exchange structure 30 with only a desired amount of hot liquid by-passing the heat exchanger while continuing to provide a convenient and automatically operable flow path for the drain cycle of the apparatus as will be explained.
  • water supplied via lines 26, 28, 29 and 31 is divided into three different flow paths.
  • the first is directly into hot water basin 20 via by-pass line 56 having partially opened valve 58 therein.
  • the second path is through the drain orifice 44 of header 34.
  • the third path is into the weir box 38 for overflow therefrom or gravitation through orifice 42.
  • any suspended solid particles which would tend to clog up the finned tubes 32 and 37 are collected in header 34 and drain therefrom through orifice 44 since the latter is of greater size than the inlet openings 54 of the individual tubes 32.
  • hot water to be cooled may be supplied outboard of the cooling tower 10 rather than inboard as illustrated in FIG. 1, without affecting operation of the hydraulic flow-segregation system.
  • the header 134 is possibly of somewaht greater size to permit the supply line 131 to be joined thereto in underlying relationship to the weir box 138, this makes no discernable change in the operation of the equipment with the overflow from the open top of weir box 138 simply cascading down over line 131 into the underlying collection basin 20.
  • FIG. 4 of the drawings is a schematic illustration of the use of the present hydraulic flow-segregation system for a single pass heat exchanger wherein water to be cooled is delivered to the reverse flow manifold header 136 via supply conduit 132 (actually in the plane of finned tubes 137 rather than as shown for purposes of clarity as being to one side thereof) whereupon the water from header 136 flows downwardly into the weir box 138 for discharge therefrom in the same manner as previously described.
  • fluid conveying structure for bringing the fluid into thermal interchange relationship with cooling air and including separate intercommunicating sections for conveying the fluid to be cooled in first one direction and then another direction relative to said cooling air;
  • a heat exchanger as set forth in claim 4 wherein is provided an atmospheric weir box communicating with said other section at the lower end thereof and provided with said other section at the lower end thereof and provided with an overlfow opening and a drain orifice therebelow, said opening being larger than the drain orifice, the means for supplying fluid to the one section including a header communicating with the lower end of the one section and provided with a fluid inlet opening and a drain orifice therebelow, the fluid inlet opening being larger than the header drain orifice, and a fluid conveying line communicating with the fluid inlet of said header for supplying fluid to be cooled thereto.
  • a heat exchanger as set forth in claim 6 wherein is provided a by-pass drain line connected to said supply line and provided with a fluid flow control valve in operable association therewith for permitting selective variation of the flow of fluid from the supply line through said by-pass drain line.
  • said header and the by-pass line for receiving flow of fluid from the same.
  • fluid conveying structure for bringing the fluid into thermal interchange relationship with cooling air and having an upper fluid inlet and a fluid outlet therebelow for gravitational fluid flow therefrom;
  • a heat exchanger as set forth in claim 10 wherein said means for effecting draining of the structure includes a weir unit at the outlet end of said structure and operable to permit gravitational draining of fluid from the structure and said weir unit in response to interruption of the supply of fluid to the structure.
  • a heat exchanger as set forth in claim 12 wherein said means for effecting draining of the structure includes a weir box at the outlet end of said structure and having an overflow opening adjacent the level of said outlet end of the structure, said weir box being provided with an orifice in the lower portion thereof for gravitational draining of fluid from the weir box.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US00264150A 1972-06-19 1972-06-19 Hydraulic flow distribution system for multiple pass air cooled heat exchanger Expired - Lifetime US3782451A (en)

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US26415072A 1972-06-19 1972-06-19

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JP (1) JPS5632553B2 (enrdf_load_stackoverflow)
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Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3865911A (en) * 1973-05-03 1975-02-11 Res Cottrel Inc Cooling tower type waste heat extraction method and apparatus
US3899553A (en) * 1973-07-27 1975-08-12 Ecodyne Corp Cooling tower plume control
US3994999A (en) * 1973-01-26 1976-11-30 Phelps Peter M Combination wet-dry cooling tower
US4003970A (en) * 1974-11-02 1977-01-18 Balcke-Durr Aktiengesellschaft Combined wet and dry heat transfer system and method for cooling towers
US4022853A (en) * 1974-10-30 1977-05-10 Gea Luftkuhlergesellschaft Happel Gmbh & Co. Kg Installation for changing the temperature of fluid media, particularly for cooling liquids and condensing vapors with air
US4032604A (en) * 1972-09-05 1977-06-28 The Marley Cooling Tower Company Hot water supply and distribution structure for cooling towers
US4098854A (en) * 1976-01-23 1978-07-04 Gea Luftkuhlergesellschaft Happel Gmbh & Co. Kg Combined wet and dry liquid cooling system and method
US4182404A (en) * 1977-12-27 1980-01-08 Fiat-Allis Construction Machinery, Inc. Radiator top tank with plural sump lines
US4194889A (en) * 1977-03-11 1980-03-25 Metallgesellschaft Aktiengesellschaft Method of and apparatus for processing sulfur-containing exhaust gas
US4237969A (en) * 1979-05-21 1980-12-09 Southern California Gas Company Heat transfer element to replace electrical heating element
US4296802A (en) * 1975-06-16 1981-10-27 Hudson Products Corporation Steam condensing apparatus
US4301861A (en) * 1975-06-16 1981-11-24 Hudson Products Corporation Steam condensing apparatus
US4964977A (en) * 1988-04-08 1990-10-23 Shinwa Sangyo Company, Ltd. Cross-flow type cooling tower
FR2882135A1 (fr) * 2005-02-17 2006-08-18 Jacir Air Traitement Sa Tour de refroidissement hybride et batterie anti-panache associee
US20090211736A1 (en) * 2008-01-28 2009-08-27 Aoki Kensuke Coolant circulating apparatus, and cooling apparatus including the same coolant circulating apparatus for electric and/or electronic device which generates heat
US20120001352A1 (en) * 2010-07-02 2012-01-05 Baltimore Aircoil Company, Inc. Induced draft cooling tower
US20140076518A1 (en) * 2012-09-19 2014-03-20 John Edwards Heat exchange system and method of use
US8711563B2 (en) 2011-10-25 2014-04-29 International Business Machines Corporation Dry-cooling unit with gravity-assisted coolant flow
CN104329959A (zh) * 2014-10-13 2015-02-04 双良节能系统股份有限公司 干湿联合式空气冷却塔
CN104329958A (zh) * 2014-10-13 2015-02-04 双良节能系统股份有限公司 垂直管降膜蒸发冷却塔
US20180238625A1 (en) * 2012-03-16 2018-08-23 Evapco, Inc. Hybrid cooler with bifurcated evaporative section
US20220170699A1 (en) * 2019-04-18 2022-06-02 Guntner GMBH & co. KG Heat exchanger arrangement having at least one multipass heat exchanger and method for operating a heat exchanger arrangement
US20220205724A1 (en) * 2019-04-18 2022-06-30 Guntner GMBH & co. KG Heat exchanger assembly having at least one multi-pass heat exchanger and method for operating a heat exchanger assembly

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JPS54161061U (enrdf_load_stackoverflow) * 1978-04-11 1979-11-10
US9023145B2 (en) 2008-02-12 2015-05-05 Bunge Amorphic Solutions Llc Aluminum phosphate or polyphosphate compositions

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US2891773A (en) * 1954-12-22 1959-06-23 Licencia Talalmanyokat Apparatus for filling and emptying air-cooled condensers
US3179164A (en) * 1961-05-10 1965-04-20 Licencia Talalmanyokat Anti-icing arrangements for heat exchangers of air condensing apparatus
US3231013A (en) * 1961-01-27 1966-01-25 Licencia Talalmanyokat Controlling the heat exchangers of air condensation apparatus

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JPS4526251Y1 (enrdf_load_stackoverflow) * 1967-10-11 1970-10-14
US3782453A (en) * 1972-06-19 1974-01-01 Marley Co Siphon breaking vent manifold for multiple pass heat exchanger

Patent Citations (3)

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Publication number Priority date Publication date Assignee Title
US2891773A (en) * 1954-12-22 1959-06-23 Licencia Talalmanyokat Apparatus for filling and emptying air-cooled condensers
US3231013A (en) * 1961-01-27 1966-01-25 Licencia Talalmanyokat Controlling the heat exchangers of air condensation apparatus
US3179164A (en) * 1961-05-10 1965-04-20 Licencia Talalmanyokat Anti-icing arrangements for heat exchangers of air condensing apparatus

Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4032604A (en) * 1972-09-05 1977-06-28 The Marley Cooling Tower Company Hot water supply and distribution structure for cooling towers
US3994999A (en) * 1973-01-26 1976-11-30 Phelps Peter M Combination wet-dry cooling tower
US3865911A (en) * 1973-05-03 1975-02-11 Res Cottrel Inc Cooling tower type waste heat extraction method and apparatus
US3899553A (en) * 1973-07-27 1975-08-12 Ecodyne Corp Cooling tower plume control
US4022853A (en) * 1974-10-30 1977-05-10 Gea Luftkuhlergesellschaft Happel Gmbh & Co. Kg Installation for changing the temperature of fluid media, particularly for cooling liquids and condensing vapors with air
US4003970A (en) * 1974-11-02 1977-01-18 Balcke-Durr Aktiengesellschaft Combined wet and dry heat transfer system and method for cooling towers
US4296802A (en) * 1975-06-16 1981-10-27 Hudson Products Corporation Steam condensing apparatus
US4301861A (en) * 1975-06-16 1981-11-24 Hudson Products Corporation Steam condensing apparatus
US4098854A (en) * 1976-01-23 1978-07-04 Gea Luftkuhlergesellschaft Happel Gmbh & Co. Kg Combined wet and dry liquid cooling system and method
US4194889A (en) * 1977-03-11 1980-03-25 Metallgesellschaft Aktiengesellschaft Method of and apparatus for processing sulfur-containing exhaust gas
US4182404A (en) * 1977-12-27 1980-01-08 Fiat-Allis Construction Machinery, Inc. Radiator top tank with plural sump lines
US4237969A (en) * 1979-05-21 1980-12-09 Southern California Gas Company Heat transfer element to replace electrical heating element
US4964977A (en) * 1988-04-08 1990-10-23 Shinwa Sangyo Company, Ltd. Cross-flow type cooling tower
FR2882135A1 (fr) * 2005-02-17 2006-08-18 Jacir Air Traitement Sa Tour de refroidissement hybride et batterie anti-panache associee
US20090211736A1 (en) * 2008-01-28 2009-08-27 Aoki Kensuke Coolant circulating apparatus, and cooling apparatus including the same coolant circulating apparatus for electric and/or electronic device which generates heat
US20120001352A1 (en) * 2010-07-02 2012-01-05 Baltimore Aircoil Company, Inc. Induced draft cooling tower
US8434746B2 (en) * 2010-07-02 2013-05-07 Baltimore Aircoil Company, Inc. Induced draft cooling tower
US9013872B2 (en) 2011-10-25 2015-04-21 International Business Machines Corporation Dry-cooling unit with gravity-assisted coolant flow
US8711563B2 (en) 2011-10-25 2014-04-29 International Business Machines Corporation Dry-cooling unit with gravity-assisted coolant flow
US20180238625A1 (en) * 2012-03-16 2018-08-23 Evapco, Inc. Hybrid cooler with bifurcated evaporative section
US10962292B2 (en) * 2012-03-16 2021-03-30 Evapco, Inc. Hybrid cooler with bifurcated evaporative section
US20140076518A1 (en) * 2012-09-19 2014-03-20 John Edwards Heat exchange system and method of use
CN104329959A (zh) * 2014-10-13 2015-02-04 双良节能系统股份有限公司 干湿联合式空气冷却塔
CN104329958A (zh) * 2014-10-13 2015-02-04 双良节能系统股份有限公司 垂直管降膜蒸发冷却塔
CN104329959B (zh) * 2014-10-13 2016-04-27 双良节能系统股份有限公司 干湿联合式空气冷却塔
CN104329958B (zh) * 2014-10-13 2016-05-11 双良节能系统股份有限公司 垂直管降膜蒸发冷却塔
US20220170699A1 (en) * 2019-04-18 2022-06-02 Guntner GMBH & co. KG Heat exchanger arrangement having at least one multipass heat exchanger and method for operating a heat exchanger arrangement
US20220205724A1 (en) * 2019-04-18 2022-06-30 Guntner GMBH & co. KG Heat exchanger assembly having at least one multi-pass heat exchanger and method for operating a heat exchanger assembly
US11976883B2 (en) * 2019-04-18 2024-05-07 Gunter Gmbh & Co. Kg Heat exchanger assembly having at least one multi-pass heat exchanger and method for operating a heat exchanger assembly
US12117249B2 (en) * 2019-04-18 2024-10-15 Guntner GMBH & co. KG Heat exchanger arrangement having at least one multipass heat exchanger and method for operating a heat exchanger arrangement

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JPS5632553B2 (enrdf_load_stackoverflow) 1981-07-28
DE2306689A1 (de) 1974-01-17
JPS4967240A (enrdf_load_stackoverflow) 1974-06-29

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