US3612172A - Air-cooled condenser - Google Patents

Air-cooled condenser Download PDF

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Publication number
US3612172A
US3612172A US859829A US3612172DA US3612172A US 3612172 A US3612172 A US 3612172A US 859829 A US859829 A US 859829A US 3612172D A US3612172D A US 3612172DA US 3612172 A US3612172 A US 3612172A
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United States
Prior art keywords
pipes
pipe
steam
condensate
header
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Expired - Lifetime
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US859829A
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English (en)
Inventor
Dietrich Dohnt
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Borsig GmbH
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Borsig GmbH
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • F28B9/005—Auxiliary systems, arrangements, or devices for protection against freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • F28B2001/065—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium with secondary condenser, e.g. reflux condenser or dephlegmator
    • 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
    • Y10S165/184—Indirect-contact condenser
    • Y10S165/197—Indirect-contact condenser including means for removing condensate from vapor flow path to bypass portion of vapor flow path

Definitions

  • a fan causes cooling air to pass over the pipes which, for efficient heat transfer, may be AIR-COOLED CONDENSER
  • the present invention relates to a condenser which is cooled by an automatically moved airflow, and in which there are provided at least two rows of substantially parallel condenser pipes spaced from each other and located one behind the other when looking in the direction of flow of the cooling air.
  • the present invention concerns an aircooled condenser of the above-mentioned type in which the rows of condenser pipes are in parallel arrangement connected to steam-distributing chambers common thereto and are in communication with condensate collecting chambers.
  • the round or profiled condenser pipes which are in most instances of the same design, are, as a rule, equipped with fins.
  • the condenser pipes are acted upon by a cool airflow which is drawn from the atmosphere and is automatically put into motion by a fan.
  • condensers are so operated that the stream to be condensed flows from the top into or about the pipes, and the condensate flows in the direction of the steam downwardly into the condensate collector.
  • Air-cooled condenser installations of the above-mentioned type especially such for depositing turbine exhaust steam with finned pipe bundles which at the upper end are connected to a common steam-distributing pipe system so that the steam and the condensate in each pipe can flow inone direction only, namely, from the top downwardly, and with cooling air temperatures below the freezing point cause considerable disturbances in the operation for instance in the vacuum installation.
  • the condensation temperature is generally at 60 C. and in most instances even lower which means that the temperature distance between the water steam condensate and the freezing point thereof is relatively small.
  • the condensate flows along the inner pipe wall downwardly to the mouth of the pipe into the condensate chamber.
  • a control of the quantity of cooling air or the turning off of cooling surfaces may at less low outer air temperatures result in a slight improvement, however, at surrounding temperatures approximately from -5 C. on, the less mentioned step is not effective against formation of ice in the pipes.
  • Noncontrollable wind influences increase the icing danger in winter considerably.
  • Ice plugs which may form may even burst the pipes with the result that air will break in. Under certain circumstances, it may then be necessary to disassemble the installation.
  • Condensers have become known in which the exhaust steam line is so arranged that the steam can enter the mouth of the finned pipes only from below, and in which the condensate flows downwardly in countercurrent flow to the upwardly flowing steam, into the condensate collecting chambers.
  • This arrangement of the exhaust steam line which is also known as dephlegmatoric circuit, prevents the undercooling of the condensate by the fact that the upwardly flowing warm steam keeps warm the condensate which flows in opposite direction.
  • this circuit can be employed only under certain conditions of operation, but wherever it can be employed, it will safely prevent ice formation in the pipes.
  • These finned pipe bundles in which the steam flows from the top downwardly while condensing, have associated therewith dephlegmator bundles which on the air side are parallel to each other and on the steam side are arranged one behind the other.
  • These subchambers are individually and adjustably connected to the air suction devices.
  • Such an arrangement is supposed to bring about that the underpressure in the succeeding subchambers decreases in the direction of the airflow whereby the steam distribution is, in conformity with the pipe rows, connected to the individual subchambers in conformity with the respective available temperature drop between steam and cooling air.
  • the condensation is supposed in this way to be completed in all pipe rows at a slight distance from where the pipe ends lead into the pertaining subchambers.
  • the length of the pipe up to the condensate discharging means in the upper subsection of the finned pipe bundle is relatively short so that also the undercooling distance at very low cooling temperatures will be reduced to a minimum.
  • FIG. 1 diagrammatically illustrates a condenser.
  • FIG. 2 represents a section taken along the line ll-ll of FIG. 1.
  • FIG. 3 represents a cross section through a condenser element on a larger scale than that ofFlG. 1.
  • the condenser according to the present invention is characterized primarily in that the steam-distributing chambers and pipelines at the upper end of the finned pipe bundle, and the steam distributor and condensate collecting chambers combined at the lower end are so connected to the bypass lines that the steam flows through the finned pipes in countercurrent direction while the finned pipes spaced at a certain distance from the upper and lower mouths of the pipes are subdivided transverse to the pipe axis into pipe sections by means of condensate withdrawing means which are connected to the central pipes which latter lead into the condensate collecting chamber.
  • the condensation of the steam is effected in two separate subsections with clear flow conditions in the pipes in countercurrent flow direction.
  • the pipe length up to the condensate withdrawing line in the upper partial section of the finned pipe bundle is relatively short so that also the undercooling distance will be reduced to a minimum at low-cooling air temperatures.
  • the condensate is detached from the upper pipe section before it is undercooled and might ice. This detachment from the inner pipe wall is effected by the condensate withdrawal means, and the detached condensate passes through the central pipes countercurrent to the upwardly flowing warm steam in the dephlegmator part, and is here held warm by the steam, which is extremely advantageous.
  • a further advantage by subdividing the finned pipe in a direction transverse to the pipe axis in two separate subsections and by the bilateral steam action consists in that the steam has available a pipe section which is large (approximately twice as large) as is available with the heretofore known condenser designs. As a result thereof, the loss in pressure of the steam when flowing into the mouth of the pipes is reduced and thereby an economic vacuum is realized. Particularly during the summer season, the heretofore known condensers have a poor vacuum because they lack the abovementioned advantage.
  • a further important advantage of the present invention over heretofore known structures consists in that not only the steam side is separated but also the condenser side. Due to the fact that a portion of the condensate is separated by the central pipes from the condensate flowing off from the dephlegmator part, an accumulation of condensate in the lower pipe mouth, i.e. at the steam inlet of the dephlegmator is avoided for all practical purposes.
  • a further development of the present invention consists in that the pipe sections, measured from the condensate withdrawal means to the respective pipe mouth in the lower as well as in the upper pipe sections prior to flowing into the pipe mouth are so designed that they become greater in steps. in view of this stepwise greater configuration, it will be assured that where the steam enters the finned pipe bundles, the shortest pipe length and thereby the smallest cooling surface is available to the incoming steam.
  • the finned pipe bundles which are located farthest from the steam entry have, when viewing in the flow direction of the steam, the larger cooling surface.
  • the bores are arranged slightly below the condensate withdrawal means in the central pipes so that from the lower condensate collecting chamber, the inert air is withdrawn from the upper subsection of the pipe through the pipe mouth of the central pipes in the condensate withdrawing means, as well as from the lower subsection of the pipes through the bores, and the withdrawn inert air then passes through the central pipe.
  • the dephlegmator chamber or cooling surface is better taken advantage of so that the condensate withdrawing means will be kept warm at this area.
  • the condensation in the first row of pipes when viewing in the cooling airflow direction is completed at a larger distance from the lower pipe mouth than is the case with the pipe rows therebehind.
  • the pipe sections measured from the condensate withdrawing means to the pipe mouth in the upper steam distributing chamber when seen in the flow direction of the cooling air is in each pipe row designed longer.
  • the central pipe is, in conformity with the present invention, built up of two parts.
  • the lower part with a larger diameter is connected to the combined steam distributor and condensate collecting chamber and overlaps the upper portion of the central pipe.
  • the condenser illustrated in FIGS. 1 and 2 comprises a plurality of roof-shaped condenser elements which are formed of at least one or, as illustrated, of three rows of substantially parallel finned pipe bundles l which are spaced from each other or are arranged one behind the other when viewing in the flow direction d of the cooling air.
  • Steam from below is conveyed to the finned pipe bundles 1 through the lower combined steam producing and condensate collecting chamber 5.
  • the conveying lines 3 and steam lines 2 also steam from above is conveyed to the finned pipe bundles l.
  • the pipe bundles are thus passed through by the steam in opposite direction.
  • the exhaust steam conduits may be connected to the finned pipe bundles in such a way that a portion of the steam is condensed first in the upper pipe sections and the residual steam is condensed in the lower pipe sections.
  • the supply of steam may also be effected (in a nonillustrated manner) from a gable side (FIG. 1) through only one bypass line 3 in such a way that the steam acts upon the upper and lower pipe sections parallel or in series and passes therethrough in opposite direction in conformity with the invention.
  • the pipes are, by a condensate withdrawing means 14, subdivided on the inside transverse to the pipe axis into an upper section 12a and a lower section 12 b.
  • the steam fed from above through the steam distributing chambers 4 will condense in the upper pipe section 12a, and the condensate will flow through the condensate withdrawing lines 14 and central pipes into the condensate collecting chambers 8.
  • FIG. 1 further shows the bulkheads ll of the air condensator which is supported by four supports 17 illustrated at the lower end.
  • FIG. 1 furthermore illustrates that the pipe sections, measured from the condensate withdrawing line 14 to the respective mouth of the pipes increase by steps or continuously not only in the upper but also in the lower pipe sections 12a and 12b when viewed in the flow direction a of the steam.
  • the pipe sections measured from the condensate withdrawing means 14 to the respective pipe mouth not only in the upper but also in the lower pipe sections 12a and 12b when viewed in the flow direction a of the steam may be designed stepwise smaller (not illustrated).
  • FIG. 2 shows that the roof-shaped finned pipe bundles l have a cross section forming the sides of an approximately equilateral triangle the basis of which is formed by an axial fan 18.
  • the fin-equipped pipe bundles may also be so arranged that in the direction of the pipe axis they are perpendicular with regard to the horizontally arranged fan axis (not illustrated).
  • the cooling air is, by at least one axial fan 18, conveyed from the bottom in upward direction or in reverse direction (not illustrated) and passes by the outside of the smooth or finequipped bundle 1.
  • FIG. 3 shows the subdivision of the upper pipe sections 12a which, when viewed in cooling airflow direction d are longer in each pipe row.
  • the condensate withdrawing means 14 is thus arranged closer to the condensation end in the upper pipe section 1211, because the latter is displaced as is well known in downward direction when viewing the flow direction of the cooling air.
  • the central pipe 15 comprises two parts.
  • the lower part 16 with a larger diameter is connected to the combined steam distributor and condensate collecting chamber 5, and the upper part of the central pipe 15, which has a smaller diameter, is covered up by said lower part 16 in such a way that therebetween a labyrinthlike sealing effect is obtained.
  • This subdivision of the central pipe compensates for the temperature expansions of the individual pipes.
  • a condenser having an upper header means and a lower header means, conduit means connected to said header means for supplying steam thereto, pipe bundle means connected to and extending between said header means, and fan means operable for causing cooling airflow through said pipe bundle means, a condensate discharge tube extending into each pipe of said pipe bundle means from the lower end of the respective pipe, the upper end of each discharge tube engaging the inside of the respective pipe and dividing the pipe into upper and lower axial sections whereby steam to be condensed flows in countercurrent direction simultaneously from said header means into both ends of said pipes, condensate chamber means connected to the lower'ends of said tubes to receive from said tubes the condensate from the upper sections of said pipes, the condensate from the lower sections of said pipes drawing from said pipes into said lower header means, and means for withdrawing condensate from said condensate chamber means and from said lower header means.
  • a condenser according to claim I in which said steam flows axially in said header means and the length of said pipe sections varies in increasing direction in conformity with the length of travel of the steam prior to entry into pipes along said header means to the end of the respective section.
  • a condenser according to claim 1 in which said steam flows axially in said header means and the length of said pipe sections varies in decreasing direction in conformity with the length of travel of the steam prior to entry into pipes along said header means to the end of the respective section.
  • a condenser according to claim 1 in which steam is supplied to about the middle of the length of said lower header means for flow outwardly therein toward the ends and flows from the ends thereof to the ends of said upper header means and then toward the middle of the length of said upper header means. the length of the said sections of said pipes into which steam flows progressively increasing in the direction of steam flow prior to entry into pipes through said header means.
  • each said tube has aperture means therein immediately below the region of engagement of the upper end of the tube with the respective pipe whereby inert air from both collectively withdrawn axial sections of each pipe passes into the respective condensate discharge tube and downwardly therethrough to said condensate chamber means.
  • a condenser according to claim 1 in which said pipe bundle means comprise pipe sections longer in differing pipes displaced from each other in the direction of airflow through the bundle means, the upper sections of said pipes varying in length in the direction of said airflow.
  • each of said tubes comprises a first upper portion which at its upper end engages a respective pipe and a second lower portion extending into said condensate chamber means, said respective portions being in slidable telescopic engagement and thereby compensating for differential thermal expansion of individual pipes in the condenser.
  • a condenser according to claim 1 in which said pipes individually are finned for each bundle means.
  • a condenser according to claim 6 in which said upper respectively sections of said pipes individually increase in length progressively in the direction of airflow through said pipe bundle means.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US859829A 1968-09-25 1969-09-22 Air-cooled condenser Expired - Lifetime US3612172A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19681776130 DE1776130A1 (de) 1968-09-25 1968-09-25 Luftgekuehlter Kondensator

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US3612172A true US3612172A (en) 1971-10-12

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US859829A Expired - Lifetime US3612172A (en) 1968-09-25 1969-09-22 Air-cooled condenser

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US (1) US3612172A (enrdf_load_stackoverflow)
BE (1) BE738794A (enrdf_load_stackoverflow)
CH (1) CH515473A (enrdf_load_stackoverflow)
DE (1) DE1776130A1 (enrdf_load_stackoverflow)
FR (1) FR2018823A1 (enrdf_load_stackoverflow)
GB (1) GB1211969A (enrdf_load_stackoverflow)
NL (1) NL6913740A (enrdf_load_stackoverflow)
SE (1) SE346613B (enrdf_load_stackoverflow)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4129180A (en) * 1976-12-06 1978-12-12 Hudson Products Corporation Vapor condensing apparatus
US4168742A (en) * 1978-03-27 1979-09-25 Hudson Products Corporation Tube bundle
US4177859A (en) * 1977-04-26 1979-12-11 Snamprogetti, S.P.A. Air condenser
US4300481A (en) * 1979-12-12 1981-11-17 General Electric Company Shell and tube moisture separator reheater with outlet orificing
US4691766A (en) * 1983-07-18 1987-09-08 Dieter Wurz Finned tube arrangement for heat exchangers
US4926931A (en) * 1988-11-14 1990-05-22 Larinoff Michael W Freeze protected, air-cooled vacuum steam condensers
WO1999020967A1 (en) * 1997-10-16 1999-04-29 Energiagazdálkodási Részvénytársaság Air-cooled condenser
US5950717A (en) * 1998-04-09 1999-09-14 Gea Power Cooling Systems Inc. Air-cooled surface condenser
US6029739A (en) * 1996-08-21 2000-02-29 Mitsubishi Heavy Industries, Ltd. Vehicular air conditioner
US6474272B2 (en) * 1999-08-10 2002-11-05 Gea Energietechnik Gmbh Apparatus for condensation of steam
US20060086490A1 (en) * 2004-10-21 2006-04-27 Fay H P Fin tube assembly for air-cooled condensing system and method of making same
US20060086092A1 (en) * 2004-10-21 2006-04-27 Fay H P Air-cooled condensing system and method
US20100206530A1 (en) * 2007-09-18 2010-08-19 Gea Energietechnik Gmbh Air-supplied dry cooler
CN101968322A (zh) * 2010-10-28 2011-02-09 北京市京海换热设备制造有限责任公司 板片式空冷系统
RU2434192C1 (ru) * 2010-04-16 2011-11-20 Открытое акционерное общество "КуйбышевАзот" Поверхностный конденсатор
US20140251589A1 (en) * 2013-03-07 2014-09-11 Spx Cooling Technologies, Inc Air cooled condenser apparatus and method
US20160102917A1 (en) * 2014-10-08 2016-04-14 Spx Cooling Technologies, Inc. Modular air cooled condenser flow converter apparatus and method
US20180128558A1 (en) * 2015-04-23 2018-05-10 Shandong University Columnar cooling tube bundle with wedge-shaped gap
EP3355024A1 (en) * 2017-01-30 2018-08-01 SPX Dry Cooling Belgium sprl Air-cooled condenser with air-flow diffuser
CN111288814A (zh) * 2020-02-18 2020-06-16 暨南大学 串联式空湿混合冷却系统、空冷岛系统及冷却方法
US10907900B2 (en) 2018-09-07 2021-02-02 Evapco, Inc. Advanced large scale field-erected air cooled industrial steam condenser
US11098963B2 (en) 2019-05-29 2021-08-24 Ovh Heat exchanger assembly and method of assembly thereof
US11105565B2 (en) 2019-05-29 2021-08-31 Ovh Heat exchanger assembly
US11112180B2 (en) 2012-05-23 2021-09-07 Spg Dry Cooling Usa Llc Modular air cooled condenser apparatus and method
US11493277B2 (en) 2019-11-06 2022-11-08 Carrier Corporation Microchannel heat exchanger

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1135516B (it) * 1981-02-18 1986-08-27 Nuovo Pignone Spa Condensatore perfezionato di vapore con raffreddamento ad aria
EP0170753A1 (fr) * 1984-07-30 1986-02-12 Hamon-Sobelco S.A. Aérocondenseur à ventilation forcée
RU2131104C1 (ru) * 1996-11-22 1999-05-27 Олег Ошеревич Мильман Воздушно-конденсационная установка
HU9700240D0 (en) * 1997-01-27 1997-03-28 Energiagazdalkodasi Intezet Air-cooled steam condenser
CN102425957A (zh) * 2011-11-24 2012-04-25 华北电力大学 一种换热板束倾斜布置的板式蒸发空冷凝汽器
CN107543427B (zh) * 2017-09-15 2019-05-14 双良节能系统股份有限公司 一种直接空冷凝汽器防冻控制方法

Citations (4)

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DE255445C (enrdf_load_stackoverflow) *
US1890185A (en) * 1928-07-14 1932-12-06 Babcock & Wilcox Co Heat transfer device
GB908429A (en) * 1958-05-12 1962-10-17 Happel Gmbh Air-cooled surface-condenser
US3450197A (en) * 1965-02-06 1969-06-17 Ferodo Sa Heat exchangers

Patent Citations (4)

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Publication number Priority date Publication date Assignee Title
DE255445C (enrdf_load_stackoverflow) *
US1890185A (en) * 1928-07-14 1932-12-06 Babcock & Wilcox Co Heat transfer device
GB908429A (en) * 1958-05-12 1962-10-17 Happel Gmbh Air-cooled surface-condenser
US3450197A (en) * 1965-02-06 1969-06-17 Ferodo Sa Heat exchangers

Cited By (37)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4129180A (en) * 1976-12-06 1978-12-12 Hudson Products Corporation Vapor condensing apparatus
US4177859A (en) * 1977-04-26 1979-12-11 Snamprogetti, S.P.A. Air condenser
US4168742A (en) * 1978-03-27 1979-09-25 Hudson Products Corporation Tube bundle
US4300481A (en) * 1979-12-12 1981-11-17 General Electric Company Shell and tube moisture separator reheater with outlet orificing
US4691766A (en) * 1983-07-18 1987-09-08 Dieter Wurz Finned tube arrangement for heat exchangers
US4926931A (en) * 1988-11-14 1990-05-22 Larinoff Michael W Freeze protected, air-cooled vacuum steam condensers
US6029739A (en) * 1996-08-21 2000-02-29 Mitsubishi Heavy Industries, Ltd. Vehicular air conditioner
RU2208750C2 (ru) * 1997-10-16 2003-07-20 Энергиагаздалкодаши Ресвенитаршашаг Конденсатор с воздушным охлаждением
WO1999020967A1 (en) * 1997-10-16 1999-04-29 Energiagazdálkodási Részvénytársaság Air-cooled condenser
US6332494B1 (en) 1997-10-16 2001-12-25 Energiagazdalkodasi Reszvenytarsasag Air-cooled condenser
US5950717A (en) * 1998-04-09 1999-09-14 Gea Power Cooling Systems Inc. Air-cooled surface condenser
US6474272B2 (en) * 1999-08-10 2002-11-05 Gea Energietechnik Gmbh Apparatus for condensation of steam
US20060086490A1 (en) * 2004-10-21 2006-04-27 Fay H P Fin tube assembly for air-cooled condensing system and method of making same
US20060086092A1 (en) * 2004-10-21 2006-04-27 Fay H P Air-cooled condensing system and method
WO2006047209A1 (en) * 2004-10-21 2006-05-04 Gea Power Cooling Systems, Inc. Air-cooled condensing system and method
US7096666B2 (en) 2004-10-21 2006-08-29 Gea Power Cooling Systems, Llc Air-cooled condensing system and method
US7243712B2 (en) 2004-10-21 2007-07-17 Fay H Peter Fin tube assembly for air-cooled condensing system and method of making same
US20100206530A1 (en) * 2007-09-18 2010-08-19 Gea Energietechnik Gmbh Air-supplied dry cooler
US8726975B2 (en) * 2007-09-18 2014-05-20 Gea Energietechnik Gmbh Air-supplied dry cooler
RU2434192C1 (ru) * 2010-04-16 2011-11-20 Открытое акционерное общество "КуйбышевАзот" Поверхностный конденсатор
CN101968322A (zh) * 2010-10-28 2011-02-09 北京市京海换热设备制造有限责任公司 板片式空冷系统
US11662146B2 (en) 2012-05-23 2023-05-30 Spg Dry Cooling Usa Llc Modular air cooled condenser apparatus and method
US11112180B2 (en) 2012-05-23 2021-09-07 Spg Dry Cooling Usa Llc Modular air cooled condenser apparatus and method
US20140251589A1 (en) * 2013-03-07 2014-09-11 Spx Cooling Technologies, Inc Air cooled condenser apparatus and method
US9354002B2 (en) * 2013-03-07 2016-05-31 Spx Cooling Technologies, Inc. Air cooled condenser apparatus and method
US20160102917A1 (en) * 2014-10-08 2016-04-14 Spx Cooling Technologies, Inc. Modular air cooled condenser flow converter apparatus and method
US20180128558A1 (en) * 2015-04-23 2018-05-10 Shandong University Columnar cooling tube bundle with wedge-shaped gap
US10408551B2 (en) * 2015-04-23 2019-09-10 Shandong University Columnar cooling tube bundle with wedge-shaped gap
EP3355024A1 (en) * 2017-01-30 2018-08-01 SPX Dry Cooling Belgium sprl Air-cooled condenser with air-flow diffuser
WO2018138147A1 (en) * 2017-01-30 2018-08-02 Spx Dry Cooling Belgium Air-cooled condenser with air-flow diffuser
CN110234953A (zh) * 2017-01-30 2019-09-13 比利时斯派奇干式冷却公司 具有气流扩散器的空冷式冷凝器
US10976106B2 (en) 2017-01-30 2021-04-13 Spg Dry Cooling Belgium Air-cooled condenser with air-flow diffuser
US10907900B2 (en) 2018-09-07 2021-02-02 Evapco, Inc. Advanced large scale field-erected air cooled industrial steam condenser
US11105565B2 (en) 2019-05-29 2021-08-31 Ovh Heat exchanger assembly
US11098963B2 (en) 2019-05-29 2021-08-24 Ovh Heat exchanger assembly and method of assembly thereof
US11493277B2 (en) 2019-11-06 2022-11-08 Carrier Corporation Microchannel heat exchanger
CN111288814A (zh) * 2020-02-18 2020-06-16 暨南大学 串联式空湿混合冷却系统、空冷岛系统及冷却方法

Also Published As

Publication number Publication date
DE1776130A1 (de) 1970-10-01
SE346613B (enrdf_load_stackoverflow) 1972-07-10
GB1211969A (en) 1970-11-11
BE738794A (enrdf_load_stackoverflow) 1970-02-16
NL6913740A (enrdf_load_stackoverflow) 1970-03-31
FR2018823A1 (enrdf_load_stackoverflow) 1970-06-26
CH515473A (de) 1971-11-15

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