US3520521A - Heavy duty condenser - Google Patents

Heavy duty condenser Download PDF

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Publication number
US3520521A
US3520521A US796287*A US3520521DA US3520521A US 3520521 A US3520521 A US 3520521A US 3520521D A US3520521D A US 3520521DA US 3520521 A US3520521 A US 3520521A
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United States
Prior art keywords
steam
channels
condenser
gas
water
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Expired - Lifetime
Application number
US796287*A
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English (en)
Inventor
Laszlo Heller
Laszlo Forgo
Arpad Bakay
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KOMPLEX NAGYBERENDEZESEK EXPORT IMPORT VALLALATA
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KOMPLEX NAGYBERENDEZESEK EXPORT IMPORT VALLALATA
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B3/00—Condensers in which the steam or vapour comes into direct contact with the cooling medium
    • F28B3/04—Condensers in which the steam or vapour comes into direct contact with the cooling medium by injecting cooling liquid into the steam or vapour
    • 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
    • F28B1/02—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using water or other liquid 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
    • F28B9/10—Auxiliary systems, arrangements, or devices for extracting, cooling, and removing non-condensable gases

Definitions

  • This invention relates to steam heated heat exchangers, more particularly condensers, provided with means for abducting noncondensing gases therefrom.
  • Heat power engineering uses various apparatus in the interior of which steam is condensed in consequence of heat exchange.
  • the precipitation issuing from the steam as well as noncondensing gases present in the interior of the apparatus have to be removed therefrom so as to ensure heat exchange continuity.
  • Whatever steam is employed for operating an apparatus the density of the resulting precipitation is always a multiple of the steam density. Accordingly, the precipitation collects at the bottom of steam chambers so that its abduction is feasible without diificulties.
  • the density of noncondensing gases only very slightly differs from the density of mostly employed steams, wherefore such gases are very difficult to remove from steam chambers without a substantial amount of steam being withdrawn together therewith.
  • the main object of the present invention is to exactly predetermine where noncondensing gases shall reliably be abducted.
  • the invention consists in that the condensing portion of the steam chamber of a heat exchanger is subdivided by juxtaposed partitions so as to form gas channels one extremity of which is open to receive steam to be precipitated whereas its other extremity is closed so as to prevent a steam flow, the steam channels having each a gas abducting passage near their closed extremity the discharge area of which is relatively narrow with respect to the cross-sectional area of its associated steam channel.
  • the extremity of the steam channels being closed for a steam flow, as much steam can penetrate into each channel as is capable to precipitate there.
  • this amount depends on the number of cooling pipes which cross the individual channels, and on the amount and temperature of cooling water flowing therethrough.
  • the amount of steam capable of precipitating in the individual steam channels is dependent on the amount and temperature of the cooling water injected into the channels. Accordingly, the ratio between the inlet cross-sectional areas of the individual steam channels and the amount of cooling water injected thereinto should be equal to the ratio between the common inlet cross-sectional area of all steam channels and the total amount of cooling water supplied into the condenser. Thereby, the same inlet flow speed of steam in each channel is obtained independent of turbulences which are unavoidable at the inlet stubs of mixing condensers.
  • the steam channels may have cross-sectional areas contracting from their open extremities to their closed ones.
  • cold cooling water may be introduced and the mixture of steam and gasrnore and more enriched with noncondensing gases-may be led in counter-current with such cooling water in a direction towards said gas abducting passages which may be connected by one or several gas pipes with a common outlet stub and vacuum pump.
  • the noncondensing gases will preferably be abducted uniformly from the group of steam channels for which purpose the cross-sectional area of the gas abducting pipes will be much larger than that of the gas abducting passages so that their flow resistance be considerable with respect to the How resistances in the gas pipes.
  • the precipitated steam mixed with the cooling water collects at the bottoms of the steam channels and has to be abducted therefrom for which purpose the confining walls of the channels must not prevent the water flowing towards outlet passages.
  • FIG. 1 is a perspective view of one embodiment partly in section
  • FIG. 2 shows a longitudinal sectional view of a detail of FIG. 1 on a relatively larger scale.
  • FIG. 3 is a perspective view partly in section of the other exemplified embodiment of the invention.
  • FIG. 1 shows a mixing condenser which is generally used with steam turbines.
  • the steam of a steam turbine is precipitated by direct contact with cooling water, such precipitation resulting in a condensate.
  • the dead steam of the turbine fiows vertically downwards as indicated by arrows 1 into a distribution chamber 2 which is a part of the steam chamber of the condenser.
  • Cooling water is introduced through conduits 3 the sides of which are provided with atomizing nozzles 4. Due to such nozzles 4, suitably atomized water jets 5 are present in the interior of the condenser.
  • the entering dead steam mixes with such atomized water and precipitates whereas the resulting mixture of condensate and cooling water flows down to the bottom of the condenser.
  • the precipitating steam is bifurcated by each conduit 3 and subdivided between channels 6, 7, 8 and 9 confined, on the one hand, by a casing 10 of the condenser and, on the other hand, by the water conduits 3 and a partition 11 bifurcated, in turn, so as to form a pair of oblique plates 12 and thereby to contract the channels 7 and 8 in the direction 1 of steam flow.
  • the channels 6 and 9 are likewise contracted by the provision of obliquely disposed plates 13.
  • the condenser besides being longitudinally subdivided into sevcral channels 6, 7, 8, 9 by said water conduits 3 and by the partition 11, comprises transverse partitions 14 as well which form with the former channels subdividing the total cross sectioned area of the condenser.
  • the flow velocity of the steam flowing into the condenser in direction 1 is not uniform as regards the whole of such cross-sectional area. This is partly due to the outlet speed of the steam being already nonuniform in the last crown of blades of the turbine.
  • turbulences appear in the pipe conduit which connects the turbine with the condenser and in which sharp directional changes are inevitable.
  • the individual channels would receive various amounts of steam independent of the amount of water in the water jets and, thus, independent of the amount of steam which the individual channels are capable to precipitate.
  • Such steam returned at the bottom of the condenser would try to flow from below into channels which receive less steam from above and, therefore, have more cooling water present than needed for precipitating the steam therein.
  • the channels 6, 7, 8, 9 may be arranged so that they do not communicate at their lower extremities as regards steam.
  • a water level 15 is maintained in the steam chamber by damming the mixture of condensate and cooling water prior to its flowing out. Therefore, pumping out of water from the condenser is regulated in such a manner as to keep the water level 15 constant.
  • the walls 12, 13, 14 of the channels 6, 7, 8, 9 will penetrate downwards below the water level 15 as shown in FIG. 1. Plates 16 fixed to the bottom of the water conduits 3 serves to separate the steam chamber 6, 7, 8 and 9 from one another. They likewise penetrate below the water level 15.
  • the mixture of condensate and cooling water collects in a chamber 17 at the bottom of the condenser.
  • the plates 12, 13, 14 and 16 obviously must not extend to the bottom of the condenser since then no flow of water would take place in the direction of arrow 18.
  • the juxtaposed steam channels closed at their end as regards steam fiow receive each an amount of steam which will be able to precipitate there in accordance with the amount of injected cooling water. Dif- 4 ferences in steam velocities otherwise always experienced at the inlet cross-sectional areas of condensers are compensated thereby.
  • noncondensing gases may be withdrawn from the individual steam channels 6, 7, 8 and 9. This is, in the instant case, obtained by gas abducting passages 19 associated each with an individual channel 6, 7, 8 and 9 and connected by a common gas pumping conduit 20 (see FIG. 2).
  • the water conduits 3 are constantly full with cold cooling water so that-through water spray nozzles 21 disposed in their walls-water is injected into chambers 22 and 23 which, actually, are the ends of the steam channels 6, 7, 8 and 9 and are partly separated from one another by a tray 24.
  • the mixture drops onto trays 25 and, therefrom, into the water collecting in the bottom 17 of the condenser.
  • gas abducting conduits 20 extend through the whole length of the condenser and of the cooling water conduits 3, and are connected through the wall of the condenser to an air pump, not shown. With the represented exemplified embodiment there are a pair of such gas abducting channels 20 the number of which may, however, be higher or lower as the case may be.
  • each steam channel 6, 7, 8, 9 requires at least one gas abducting passage 19, obviously a plurality of such passages has to be employed.
  • the crosssectional area of the gas abducting channels 20 will be at least the double of the total cross-sectional area of the gas abducting passages 19 whereby a uniform withdrawal of the noncondensing gases is obtained.
  • Gas abduction as described above becomes selfregulating, viz, if a lower amount of air flowed through one of the gas abducting channels 20 than through others, the resistance against the flow of air in the first mentioned gas abducting channel 20 at the gas abducting or inlet passage 19 would diminish and thereby the amount of abducted gas be automatically increased.
  • the resistance against the flow of air in the first mentioned gas abducting channel 20 at the gas abducting or inlet passage 19 would diminish and thereby the amount of abducted gas be automatically increased.
  • FIG. 3 shows an exemplified embodiment of the heat exchanger apparatus according to the invention in the form of a surface condenser likewise used with steam turbines.
  • Dead steam withdrawing from a steam turbine enters the distribution chamber 2 provided in the upper portion of the condenser in the direction of the arrows 1.
  • the cooling water required for precipitating the steam flows through pipe conduits 28 and the steam precipitates also on the outer surface of the latter.
  • the chamber occupied by the cooling water pipe conduits 28 is subdivided on the one hand by the longitudinal partition 11 and, on the other hand, by transversal partitions 14 into juxtaposed channels 31 and 32. All partitions extend from the bottom portion of the distribution chamber 2 below the water surface level 15 maintained in the bottom portion of the condenser.
  • the water collected here withdraws through an outlet stub as indicated by the arrow 18.
  • the steam channels 31 and 32 are again open at the top.
  • Partitions 29 disposed near the closed extremities of the steam channels 31 and 32 confine chambers 30 separated from other portions of the channels and penetrated likewise by pipe conduits 28 of cooling water.
  • a heavy duty condenser comprising, in combination, a casing enclosing a steam chamber between an inlet stub and an outlet stub, a distribution chamber in the upper portion of said casing and communicating with said inlet stub, a water chamber in the lower portion of said casing and communicating with said outlet stub, a plurality of longitudinal and transverse partitions extending from the side Walls of said casing between said distribution chamber and said water chamber, each partition extending so as to reach below the surface of water permitted to collect in said water chamber but above the bottom wall of said casing, said partitions defining a plurality of steam channels, steam condensing means within each of said steam channels, and gas abducting channel means at the down stream extremities of and communicating through gas abducting passages with each of said steam channels said partitions preventing the passage of steam between said channels.
  • a heavy duty condenser as recited in claim 4 including overlapping tray means disposed in said upwardly extending portion of each of said steam channel means, discharge areas remaining between said tray means and said partitions to permit a discharge of water from said tray means and the upward passage of remaining steam and gas.
  • a heavy duty condenser as recited in claim 1, wherein at least one of said partitions in each of said steam channels is at least in part obliquely oriented to contract each of said steam channels in a direction of steam flow.
  • a heavy duty condenser as recited in claim 1, wherein the inlet cross sectional area of each of said steam channels is larger than the cross sectional area of the respective gas abducting passage defining the outlet of said channel.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
US796287*A 1964-11-06 1969-01-21 Heavy duty condenser Expired - Lifetime US3520521A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
HUHE000449 1964-11-06

Publications (1)

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US3520521A true US3520521A (en) 1970-07-14

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US796287*A Expired - Lifetime US3520521A (en) 1964-11-06 1969-01-21 Heavy duty condenser

Country Status (6)

Country Link
US (1) US3520521A (de)
CH (1) CH448146A (de)
DE (1) DE1501347A1 (de)
FI (1) FI43741B (de)
GB (1) GB1109066A (de)
SE (1) SE334374B (de)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5471080A (en) * 1977-11-18 1979-06-07 Shizuoka Prefecture Liquid closeddcirculating evaporation concentration method
US4165973A (en) * 1977-06-27 1979-08-28 Stergiou Steve S Dust collector and air scrubber
EP0467878A1 (de) * 1990-07-18 1992-01-22 Energiagazdálkodási Részvénytársaság Einspritzkondensationsanlage
US6041852A (en) * 1995-12-15 2000-03-28 Kabushiki Kaisha Toshiba Condenser
US6296049B1 (en) * 1999-04-15 2001-10-02 Kabushiki Kaisha Toshiba Condenser
JP2013029228A (ja) * 2011-07-27 2013-02-07 Toshiba Corp 直接接触式復水器
WO2014045071A3 (en) * 2012-09-20 2014-05-15 Gea Egi Energiagazdálkodási Zrt. Hybrid condenser
CN108204745A (zh) * 2017-12-28 2018-06-26 安徽宏实光机电高科有限公司 一种新型冷凝回收装置

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59145484A (ja) * 1983-02-07 1984-08-20 Hitachi Ltd 復水器
FR2939877A1 (fr) * 2008-12-16 2010-06-18 Air Liquide Procede et appareil de condensation de vapeur provenant d'une turbine a vapeur
RU2520769C1 (ru) * 2012-12-25 2014-06-27 Егор Владимирович Пименов Конденсатор паровой турбины
CN111735318B (zh) * 2020-06-30 2021-05-28 武汉第二船舶设计研究所(中国船舶重工集团公司第七一九研究所) 一种海洋平台喷射式冷凝装置

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US150478A (en) * 1874-05-05 Improvement in feed-water heaters
US1372409A (en) * 1917-11-21 1921-03-22 Westing House Electric & Mfg C Condenser
US1841200A (en) * 1929-08-16 1932-01-12 Juge Sergius Von Le Preheater for boiler feed water
US1845549A (en) * 1931-06-26 1932-02-16 Westinghouse Electric & Mfg Co Condenser
US2308719A (en) * 1940-08-31 1943-01-19 Worthington Pump & Mach Corp Feed water heater
US2558222A (en) * 1946-07-27 1951-06-26 Russell W Parkinson Deaerating hot well
US2564583A (en) * 1948-09-30 1951-08-14 Worthington Pump & Mach Corp Deaerating feed-water heater
US2689018A (en) * 1951-06-11 1954-09-14 American Water Softener Co Apparatus and method for deaerating water
US2956784A (en) * 1958-07-02 1960-10-18 Maryland Shipbuilding And Dryd Apparatus for condensing and deaerating
US3158666A (en) * 1961-09-11 1964-11-24 Licencia Talalmanyokat Heavy-duty mixing condenser
US3391911A (en) * 1963-05-04 1968-07-09 Komplex Nagyberendezesek Expor Mixing condensers

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US150478A (en) * 1874-05-05 Improvement in feed-water heaters
US1372409A (en) * 1917-11-21 1921-03-22 Westing House Electric & Mfg C Condenser
US1841200A (en) * 1929-08-16 1932-01-12 Juge Sergius Von Le Preheater for boiler feed water
US1845549A (en) * 1931-06-26 1932-02-16 Westinghouse Electric & Mfg Co Condenser
US2308719A (en) * 1940-08-31 1943-01-19 Worthington Pump & Mach Corp Feed water heater
US2558222A (en) * 1946-07-27 1951-06-26 Russell W Parkinson Deaerating hot well
US2564583A (en) * 1948-09-30 1951-08-14 Worthington Pump & Mach Corp Deaerating feed-water heater
US2689018A (en) * 1951-06-11 1954-09-14 American Water Softener Co Apparatus and method for deaerating water
US2956784A (en) * 1958-07-02 1960-10-18 Maryland Shipbuilding And Dryd Apparatus for condensing and deaerating
US3158666A (en) * 1961-09-11 1964-11-24 Licencia Talalmanyokat Heavy-duty mixing condenser
US3391911A (en) * 1963-05-04 1968-07-09 Komplex Nagyberendezesek Expor Mixing condensers

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4165973A (en) * 1977-06-27 1979-08-28 Stergiou Steve S Dust collector and air scrubber
JPS5471080A (en) * 1977-11-18 1979-06-07 Shizuoka Prefecture Liquid closeddcirculating evaporation concentration method
EP0467878A1 (de) * 1990-07-18 1992-01-22 Energiagazdálkodási Részvénytársaság Einspritzkondensationsanlage
US5154227A (en) * 1990-07-18 1992-10-13 Energiagazdalkodasi Intezet Jet condenser
TR25364A (tr) * 1990-07-18 1993-03-01 Energiagazdalokodasi Intezet EGZOS BUHARINI YOGUSTURMAYA YÖNELIK PüSKüRTMELI YOGUSTURUCU
US6041852A (en) * 1995-12-15 2000-03-28 Kabushiki Kaisha Toshiba Condenser
US6296049B1 (en) * 1999-04-15 2001-10-02 Kabushiki Kaisha Toshiba Condenser
JP2013029228A (ja) * 2011-07-27 2013-02-07 Toshiba Corp 直接接触式復水器
WO2014045071A3 (en) * 2012-09-20 2014-05-15 Gea Egi Energiagazdálkodási Zrt. Hybrid condenser
CN104736957A (zh) * 2012-09-20 2015-06-24 亿吉埃冷却系统有限公司 混合冷凝器
RU2619970C2 (ru) * 2012-09-20 2017-05-22 Геа Эги Энергиагаздалькодаши Зрт. Гибридный конденсатор
CN104736957B (zh) * 2012-09-20 2017-09-15 亿吉埃冷却系统有限公司 混合冷凝器
US9897353B2 (en) 2012-09-20 2018-02-20 Gea Egi Energiagazdalkodasi Zrt. Hybrid condenser
CN108204745A (zh) * 2017-12-28 2018-06-26 安徽宏实光机电高科有限公司 一种新型冷凝回收装置

Also Published As

Publication number Publication date
CH448146A (de) 1967-12-15
DE1501347A1 (de) 1969-05-14
FI43741B (de) 1971-03-01
GB1109066A (en) 1968-04-10
SE334374B (de) 1971-04-26

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