US3280900A - Steam surface condenser - Google Patents

Steam surface condenser Download PDF

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Publication number
US3280900A
US3280900A US394001A US39400164A US3280900A US 3280900 A US3280900 A US 3280900A US 394001 A US394001 A US 394001A US 39400164 A US39400164 A US 39400164A US 3280900 A US3280900 A US 3280900A
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steam
condensate
passages
condensing
zones
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Wartenberg Kurt
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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

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  • the present invention relates to an air-cooled heattransfer device. More specifically, this invention is concerned with an air-cooled steam surface condenser that is used as part of a steam power plant cycle and wherein the steam-condensate passages as Well as the cooling-air passages are designed and arranged in such a manner that a reliable and advantageous operation of the condenser is insured.
  • Air is the gas most commonly used as cooling medium, and it has the advantage that it is anywhere and at any time available.
  • air has a relatively low heat capacity which, in conjunction with its relatively poor heat-transfer properties, requires large heat-transfer surfaces when air is used for cooling purposes.
  • condenser systems of the air-cooled type are of relatively large dimensions.
  • an aircooled heat transfer device requires that the cross-sections of the air passages be relatively large, to insure an efiicient heat transfer.
  • the air-flow path through the heat-transfer elements should be as short as possible to keep the amount of power required to draw air through the heat-transfer elements within tolerable limits.
  • the condensate and the steam flow essentially in opposite directions. That is to say, the condensate flows to a zone where the pressure is at a maximum, whereas the noncon-densable gases of the steam to be condensed are directed to a zone where the pressure is at a minimum and removed there.
  • the first arrangement has the advantage that no large amounts of materials are required for the construction of the condenser system, because the permissible steam velocities may be as high as 230 to 260 feet per second so that the cross-section of the steam zone may be made relatively small which, in turn, permits the overall dimensions of the condenser system to be made relatively small also.
  • Relatively large steam passage cross-sections are characteristic of relatively low steam velocities. However, such large cross-sections are necessary only at the steam inlet side of the heat-transfer elements, since the steam is quickly reduced in volume because of the progressive eondensation,-s-o that finally its volume is not greater than five to eight percent of the original steam volume.
  • This remaining steam volume consists essentially of noncondensable gases which are present, almost without exception, in any condenser. However, such non-condensable gases are saturated with steam so that they have to be cooled to about 5 to 9 F. below the condensing tempera- .ture to permit them to be removed as unsaturated gases by suitable means from the steam section of the condenser system.
  • Another object of the invention is to provide an aircooled surface condenser in which provision is made to prevent excessive cooling of the condensate and formation of ice.
  • Yet another object of the invention is to provide a steam surface condenser of the air-cooled type wherein the amount of material required is kept within tolerable limits.
  • Still another object of the invention is to provide a steam condenser wherein the steam passages are dimensioned in accordance with the progressive decrease in volume of the steam.
  • Another object of the invention is to provide an aircooled steam condenser that can be economically constructed.
  • a further object of the invention is to provide a heatrtransfer device in which the advantages inherent in steamcondensate circuits of the paralleland counter-flow types are utilized.
  • Another object of the invention is to design the heattransfer elements of an air-cooled steam surface condenser in such a manner that they may be prefabricated and assembled to heat-transfer units.
  • bafile plates are arranged within the steam-condensate passages whereby condensing and subcooling zones are established, the former being gradually reduced in cross-section in accordance with the progressive decrease in volume of the steam passing therethr-ough.
  • the advantages of a counter-flow arrangement wherein steam and condensate flow in opposite directions are utilized by progressively reducing the steam passages in cross-section in such a manner that at the end of the steam-flow path the crosssection of the passages is not greater than eight to ten percent of the cross-sectional area of the steam passages at the steam inlet side.
  • the subcooling zones both in parallel-flow and counter-flow arrangements of steam-condensate circuits as well as in combinations of both are formed by strip-shaped condensate collection trays or plates which are arranged in such a manner .that the subcooling zones are established in proximity to the air inlet side.
  • the baffle plates and condensate collection trays are disposed in such a manner that gravitational forces are sufficient to cause the condensate to flow to the condensate storage tanks.
  • the above-described bubbling of the condensate in steam circuits in which steam and condensate flow in opposite directions is positively prevented by sealing oif the lower portions of the steam inlet cross-section of the steam passages by seal baflles which, in conjunction with subcooling zone sealing means, define a passage through which the condensate flows to the condensate storage tank.
  • the baflle plates are arranged in such manner within the steam passages that the condensing section is subdivided into first and second condensing zones, the arrangement being such that in the first condensing zone a substantially parallel How of steam and condense is effected, whereas in the second condensing zone steam and condensate generally flow in opposite directions.
  • FIGURE 1 is a section of the condenser of the inventoon taken along line II--II in FIG. 2;
  • FIGURE 2 isa partial section and a detail view of the condenser of FIG. 1 taken along line II of FIG. 1;
  • FIGURE 3 is a detail of a portion of another embodiment of a condenser constructed in accordance with the invention.
  • FIGURE 4 is a detail of a portion of a further embodiment of a condenser constructed in accordance with the invention.
  • FIGURE 5 is a side elevation of a portion of a condensing section
  • FIGURE 6 is a top plan view of two parallel, spaced rows of heat-transfer elements serving as cooling-air channels, the arrangement being such that steam-condensate passages are established between adjacent rows of cooling-air channels;
  • FIGURE 7 is an end view of the arrangement of FIG. 6 as seen from the steam inlet side.
  • FIGURE 8 is an embodiment of a heat-transfer element of the invention.
  • FIG. 1 a horizontal steam-supply pipe 1 in FIG. 1, which is in communication with a riser 3 through pipe connecting means 2.
  • Riser 3 extends through a condensate storage tank 5 that is located uncovered beneath a steam distribution chamber 4.
  • lanes-as well as the air lanes to be described hereinafter are accommodated in a box-shaped structure having side walls '6 and being enclosed by a shell 8.
  • a supporting framework 7 carries the structures at the top of which a dome 9 is arranged which accommodates a gear unit 10 including a motor for driving an exhaust fan 1.
  • a diffuser 12 communicates with the outlet of fan 11.
  • Fan 11 draws cooling air through the condenser system as indicated by flow lines 13.
  • the steam is condensed in the box-shaped structure enclosed by side walls 6.
  • this structure is also closed at the top and bottom by end plates 14 and 14' respectively, with air lanes 15 extending therethro-ugh.
  • air passages 15' are established by rows of successive, internally finned tubes or heat-transfer elements 15, through which cooling air is directed.
  • elements 15 have a substantially rectangular cross-section.
  • Steam-condensate passages 16 are defined 'by arranging the rows of successive cooling elements I15 in parallel, spaced relationship, with passages 16 being in communication with steam distribution chamber 4 at the steam inlet side.
  • Bafile plates 17 are arranged within steam-condensate passages 16 thereby establishing upper and lower condensing zones. Baflle plates 17 are inclined with respect to the horizontal in such a manner that the steam passages are progressively reduced in cross-section in accordance with the progressive decrease in volume of steam at certain steam velocities.
  • the upper passage portions or condensing zones lead into a chamber 18 which is disposed above steam distribution chamber 4 and is in communication with subcooling zones 20 through pipe means 19.
  • Strip-shaped condensate collection trays 21 are provided to separate the lower steam passage portions from subcooling zones 20 which communicate with condensate storage tank 5 at their one end and with a space 22 between side walls 6 and shell 8 at their other end.
  • subcooling zones 20 are sealed off against steam distribution chamber 4 by seal baffles 23- which are immersed in the condensate fluid. Gases in space 22 are removed by suitable means, not shown, through gas outlets 24.
  • the exhaust steam of a power engine is fed through steam-supply pipe 1 and pipe connecting means 2 to riser 3, whence it enters steam distribution chamber 4.
  • the steam is then admitted to steam-condensate passages 16 which are subdivided into upper and lower condensing zones by bafile plates 17, with the lower condensing zones being separated tfrom the subcooling zones 20 by stripshaped condensate collection trays 21.
  • the steam-flow path through the steam condensing zones is determined by baflle plates 17 which, because of their inclined arran-gement, are effective to gradually reduce the steamflow path in area in accordance with the progressive decrease in volume of the steam in such a manner that at the place where the yet steam-saturated non-condensable gases leave steam-condensate passages 16 the cross section of the steam-flow path is about one-twelfth to The steam-condensate one-tenth the size of the cross-sectional area of the steamflow path at the inlet side.
  • the condensate running down the walls of heat-transfer elements flows over sealing baffles 23 to condensate storage tank 5, the flow being enhanced and directed by the inclined arrangement or by the geometry of collection trays 21.
  • a condensate drain pipe 25 returns the condensate to the feed system, not shown, for re-use as feed-water.
  • the noncondensable gases accumulate in chamber 18 above steam distribution chamber 4 and are directed through pipes 19 to subcooling zones 20 which :are located at the air inlet side of the condenser, that is, at the cold-air side. In subcooling zones 20 the noncondensable gases which are still saturated with steam are then cooled to about 9 F.
  • the condensate dripping from heat-transfer elements 15 into subcoolin-g zones 20 is also directed to condensate storage tank 5, entering tank 5 at the lower side of seal baffles 23.
  • the dry gases are directed to space 22 where they are removed through gas outlets 24 by suitable means not shown.
  • exhaust fan 11 operates to draw the cooling air upwards through passages 15.
  • This air circuit has the advantage that, when used in conjunction with the condenser of the invention, any effect of the ever varying atmospheric conditions, such as wind influence and solar radiation, on the efficiency of the aircontacter cooling surfaces will be eliminated.
  • the efficiency of the heat-transfer surface is determined solely by the quantity of air delivered by exhaust fan 11 or by the air velocity in the air passages. It should be understood that exhaust fan 11 has means for varying its speed.
  • FIG. 3 The embodiment shown in FIG. 3 is substantially similar to that of FIGS. 1 and 2, except for a few minor modifications.
  • parts corresponding to those shown in FIGS. 1 and 2 are provided with similar numerals followed by a superscript
  • the major difference between the two embodiments of FIGS. 1 and 3 consists in that in the embodiment of FIG. 3 the inclined arrangement of condensate collection trays 21' is reversed with respect to the arrangement of FIG. 1. In this manner, a parallel flow of steam and condensate is achieved in condensing zone 26, whereas in the following condensing zone 27 steam and condensate flow essentially in opposite directions.
  • the flow paths of the steam and condensate as controlled by baffie plates 17 and condensate collection trays 21 are indicated by arrows in FIG. 3.
  • the steam-flow path is gradually reduced in area between steam inlet 29 and area 30 where steam flow is reversed, the reduction corresponding to the progressive decrease in volume of steam as the condensation proceeds.
  • the steam velocity or variations in steam velocity have no disadvantageous effect on the operation of the condenser.
  • the cross-section of the steam-flow path is substantially equal to that at steam inlet 29.
  • the critical zone 27 is located above baffie plates 17', at the same time making provision for the steam and condensate to flow in opposite directions.
  • FIG. 4 another embodiment is shown in which provision is made to prevent the condensate from bubbling or foaming.
  • a portion of the condenser similar to that of FIG. 3 is shown.
  • no description is given here of the details in which the two portions are identical.
  • seal baffles 32 which, in conjunction with seal baffles 23, define a passage through which the condensate flows to condensate storage tank 5'.
  • Seal baffies 32 are effective to deflect the steam entering the steam-condensing passages in such a manner that part of the steams flow in vertical direction whereby the condensing of steam on the cooling surfaces is accelerated, at the same time insuring that the steam velocity immediately above the condensate stream is virtually zero, so that there is no possibility anymore for the condensate to foam up or form bubbles.
  • a condenser according to claim 5 in which the dividing plates and separating means are inclined in such a manner that gravitational forces are sufficient to cause the condensate to flow to the condensate storage means.
  • a condenser according to claim 5 in which seal bafiles are provided to seal off the lower portions of the inlet cross-sections of the steam-condensate passages against the steam distribution chamber, said seal bafiles in cooperation with the sealing means defining a passage through which the condensate flows to said condensate storage means.
  • a steam surface condenser heat-transfer elements arranged in parallel rows and adjacent rows of said heattransfer elements defining steam-condensate passages therebetween, variable fan means for drawing cooling gas through said heat-transfer elements, dividing plates disposed in said steam-condensate passages to establish lower and upper cooling zones therein separated by said dividing plates, said dividing plates being inclined with respect to the horizontal to gradually reduce said steam-condensate passages in cross-section in accordance with the progressive decrease in volume of steam passing therethrough, steam-condensate subcooling zones in communication with the upper condensing zone, separating means disposed in said steam-condensate passages for separating said lower condensing zone from the subcooling zones, a condensate storage tank, a steam distribution chamber, riser means, said lower condensing zone receiving steam from said steam distribution chamber and the steam passing from the lower to the upper zone, and the steam-condensate passages being in communication with said condensate storage means, said riser means, said
  • thermoelectric element is rectangular, internally finned tube members which, when assembled, define the steam-condensate passages.
  • a condenser according to claim 9 including side walls, a shell, and a framework, said side walls and said shell enclosing the heat-transfer elements and forming a box-shaped structure, said structure being supported by the framework and the riser 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)
US394001A 1963-09-06 1964-09-02 Steam surface condenser Expired - Lifetime US3280900A (en)

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AT718163A AT238741B (de) 1963-09-06 1963-09-06 Luftgekühlter Kondensator

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3424235A (en) * 1966-10-11 1969-01-28 Lummus Co Air-cooled condenser with provision for prevention of condensate freezing
US3430691A (en) * 1965-11-05 1969-03-04 Scholl Dr Ing Gunter High-capacity air-cooled heat exchanger
FR2345686A1 (fr) * 1976-03-23 1977-10-21 Maschf Augsburg Nuernberg Ag Echangeur de chaleur
US20030063437A1 (en) * 2001-09-28 2003-04-03 Nec Corporation Information processing unit and method for cooling same

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1159775A (en) * 1913-10-23 1915-11-09 Charles Volney Kerr Condenser.
US1406356A (en) * 1917-10-01 1922-02-14 Westinghouse Electric & Mfg Co Condenser
US1845546A (en) * 1930-12-05 1932-02-16 Westinghouse Electric & Mfg Co Condenser
US3204693A (en) * 1962-07-24 1965-09-07 Friedrich Hermann Air-cooled steam-condenser system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1159775A (en) * 1913-10-23 1915-11-09 Charles Volney Kerr Condenser.
US1406356A (en) * 1917-10-01 1922-02-14 Westinghouse Electric & Mfg Co Condenser
US1845546A (en) * 1930-12-05 1932-02-16 Westinghouse Electric & Mfg Co Condenser
US3204693A (en) * 1962-07-24 1965-09-07 Friedrich Hermann Air-cooled steam-condenser system

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3430691A (en) * 1965-11-05 1969-03-04 Scholl Dr Ing Gunter High-capacity air-cooled heat exchanger
US3424235A (en) * 1966-10-11 1969-01-28 Lummus Co Air-cooled condenser with provision for prevention of condensate freezing
FR2345686A1 (fr) * 1976-03-23 1977-10-21 Maschf Augsburg Nuernberg Ag Echangeur de chaleur
US20030063437A1 (en) * 2001-09-28 2003-04-03 Nec Corporation Information processing unit and method for cooling same

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