EP0546315B1 - Condenseur à vapeur - Google Patents

Condenseur à vapeur Download PDF

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Publication number
EP0546315B1
EP0546315B1 EP19920118798 EP92118798A EP0546315B1 EP 0546315 B1 EP0546315 B1 EP 0546315B1 EP 19920118798 EP19920118798 EP 19920118798 EP 92118798 A EP92118798 A EP 92118798A EP 0546315 B1 EP0546315 B1 EP 0546315B1
Authority
EP
European Patent Office
Prior art keywords
cooler
tubes
cooling
steam
steam condenser
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP19920118798
Other languages
German (de)
English (en)
Other versions
EP0546315A1 (fr
Inventor
Jerg Dipl.-Ing. Scheurlen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Balcke Duerr GmbH
Original Assignee
PreussenElektra AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by PreussenElektra AG filed Critical PreussenElektra AG
Publication of EP0546315A1 publication Critical patent/EP0546315A1/fr
Application granted granted Critical
Publication of EP0546315B1 publication Critical patent/EP0546315B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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

Definitions

  • the invention relates to a steam condenser with at least one tube bundle through which cooling water flows, the tubes of which are fastened at their ends in tube sheets and are supported along their length by a plurality of supporting walls Support wall result, and which is assigned a cooler for the non-condensable gases, the pipes of which are separated from the pipes above by at least one cover, the non-condensable gases, in particular air, via an exhaust line from the space formed by the cover exclusively in the Be sucked off near the tube sheet on the cooling water inlet side.
  • a steam condenser is known for example from EP-A 325 758.
  • the non-condensable gases are sucked out of the cooler over the entire length of the cooler.
  • the pressure at the end of the flow path in the condenser is higher on the cooling water outlet side than on the cooling water inlet side because the temperature difference between steam and cooling water is smaller there, i.e. less steam flows and condenses and therefore the pressure losses are smaller.
  • the difference between the pressure in the respective field of the condenser and the pressure in the suction line on the cooling water outlet side is greater than on the inlet side.
  • the non-condensable gases are therefore primarily extracted from the fields of the condenser on the cooling water outlet side, although less because of the lower condensation capacity non-condensable gases.
  • the US Pat. No. 3,349,841 discloses a steam condenser of the generic type with at least one tube bundle through which cooling water flows, the tubes of which are fastened at their ends in tube sheets and are supported along their length by a plurality of supporting walls, wherein, due to the construction, the annular gaps between the tubular jacket surface are carried out by the supporting walls as a result of the design and the inner wall of the bore in the support wall, and to which a cooler for the non-condensable gases is assigned, the pipes of which are separated from the pipes above by at least one cover, the non-condensable gases, in particular air, from those formed by the cover Only be sucked off near the tube plate on the cooling water inlet side.
  • This known device has the disadvantage that the roof-shaped air cooler in the upper half is free of cooling tubes.
  • pipe support walls are alternately provided with trapezoidal recesses on the left and right of a vertical partition.
  • This arrangement forces the steam to change from one side to the other in each section delimited by two retaining walls and to flow around cooling pipes in the process.
  • the arrangement thus has a tube-free space and large flow cross sections. This results in comparatively low speeds, as a result of which the cooling tubes are surrounded by an air envelope which extremely deteriorates the heat transfer.
  • the object of the invention is to develop a steam condenser of the generic type in such a way that the efficiency of the condenser is improved.
  • the generic steam condenser is further developed in that the annular gaps between the inner wall of the bores provided in the support walls and the lateral surface of the tubes of the cooler passed through these bores in the suction area of the cooler are larger than in the rest of the area of the cooler.
  • a condenser constructed according to the invention provides the gases to be cooled with very small flow cross sections in the area of the annular gaps, so that comparatively very high velocities and thus a particularly good heat transfer is achieved even with high air contents. Due to the ring gaps increasing towards the suction area, the volume flow can be approximated to the suction volume flow of the evacuation pump, which in a first approximation is constant, the high flow velocities guaranteeing good cooling in the smaller ring gaps in front of it.
  • the non-condensable gases are led to the coldest point of the cooler, namely in the vicinity of the cooling water inlet, before being extracted by flow along the cooler tubes, so that the greatest possible mixture subcooling takes place here, which is reduced by the residual condensation of the steam portion the proportion of the vapor extracted in relation to the total amount extracted and thus to a large proportion of non-condensable gases.
  • the total power to be installed for the extraction can be reduced as a result, and the condenser is more sensitive to possible air ingress than the known construction.
  • the flow achieved with the invention becomes non-condensable gases along the pipes in the area of the cooler.
  • the area of the annular gaps in the area of the cooler can increase from the support walls on the cooling water outlet side to the support walls on the cooling water inlet side. This takes into account that the volume of the non-condensable gases flowing in the direction of the tube sheet on the cooling water inlet side increases.
  • the area of the annular gaps can be increased either by increasing the size of the annular gaps or by increasing the number of enlarged annular gaps per supporting wall in the support walls lying towards the tube plate on the cooling water inlet side.
  • the invention further proposes to arrange an additional supporting wall for part of the cooler tubes in the region of the mouth of the suction line. This additional supporting wall prevents transverse vibrations of the pipes in the mouth area of the suction line, in particular when the condenser begins to be evacuated, in which relatively large amounts of air are drawn out of the condenser through the suction line.
  • the invention proposes to arrange in the area of the mouth of the suction line a baffle that runs parallel to the cooler tubes and extends over part of the length of the cooler tubes and is attached to the cover.
  • This baffle forms a kind of baffle for the steam-gas mixture coming from this first field and also prevents too much steam from being sucked out of the first field of the cooler, despite the greatest suction effect in this area of the condenser.
  • a cross flow of the gases to be extracted is forced through the baffle in the extraction area of the cooler.
  • a steam condenser shown in Fig. 1 shows a tube bundle indicated by dash-dotted hatched areas, which - possibly together with other tube bundles - is arranged in a condenser housing, not shown in the drawing, and steam is applied to it from above, which comes from one of the evaporation nozzles Steam turbine comes and is to be condensed in the condenser.
  • So-called steam passages are formed in order to achieve a homogeneous steam flow and the most uniform possible application of the steam condenser tubes forming the tube bundle, so that a cross section of the tube bundle results, as can be seen in FIG. 1.
  • the tube bundle forms two bundle halves 1a and 1b which are arranged symmetrically to a vertical central axis and which are triangular in cross section and which are arranged above a further bundle section 1c.
  • the bundle halves 1a and 1b and the bundle section 1c arranged steam trap plates 2.
  • a cooler 3 is provided centrally between the bundle halves 1a and 1b and the bundle section 1c, from which the non-condensable gases, in particular air, are sucked out of the steam condenser.
  • the cooler area of the steam condenser is shown enlarged in FIGS. 2 to 5.
  • the cooler 3 like the tube bundle of the steam condenser formed by the bundle halves 1a and 1b and by the bundle section 1c, is formed by tubes 4 which are fastened at their ends in tube sheets 5a, 5b without gaps.
  • tube sheets 5a, 5b can be seen in section in FIG. 3.
  • 3 also shows that the tubes 4 are supported along their length by a plurality of support walls 6, wherein when the tubes 4 are passed through these support walls 6, design-related annular gaps 10 between the outer surface of the tubes 4 and the respective support wall 6 provided with holes surrender.
  • the annular gaps 10 are drawn exaggeratedly large in FIGS. 4 and 5. They normally have a width of 0.1 to 0.2 mm, the enlarged gaps approx. 0.5 to 1 mm.
  • the tubes 4 of the cooler 3 are separated from the overlying tubes of the bundle halves 1a and 1b by a cover 7 which prevents steam to be condensed and condensate dripping from the tubes of the bundle halves 1a and 1b from above enter the cooler 3 here.
  • This cover 7 is also shown in FIG. 3.
  • the steam to be condensed which comes out of the exhaust pipe of a turbine, is introduced into the steam condenser from above. Accordingly, coming from above, it acts on the tubes of the tube bundle divided into the bundle halves 1a and 1b and into the bundle section 1c, the tubes 4 of which are flowed through by cooling water.
  • the flow of cooling water K through the pipes 4 is indicated in FIG. 3 by the horizontal arrow.
  • the condensate flows or drips down and in this way gets either to the condensate drain plates 2 or to the bottom of the condenser housing, not shown, so that it can be returned to the water-steam cycle.
  • the arrangement of the cooler 3 ensures that these are sucked out of the steam condenser in order to avoid an accumulation of these non-condensable gases in the condenser and thus a deterioration in the efficiency of the condenser. Care must be taken to ensure that as little steam as possible is sucked out of the steam condenser with the suction of the non-condensable gases in order to avoid steam losses.
  • the non-condensable gases are extracted at as central a point as possible in the steam condenser, which is protected by the cover 7 against direct exposure to steam to be condensed.
  • the proportion of steam during suction from the cooler 3 and thus the inevitable loss of steam is reduced.
  • the non-condensable gases are extracted from the space of the cooler 3 formed by the cover 7 only in the vicinity of the tube sheet 5a on the cooling water inlet side, ie in the area of the tube sheet recognizable on the left in FIG. 3 5a.
  • a suction connection 8 can be seen in the immediate vicinity of this tube sheet 5a, on the suction pipe according to FIG. 1 9 is connected. This arrangement of the suction on the inlet side of the cooling water leads the non-condensable gases to the coldest point of the cooler 3 before they are sucked off by flow along the pipes 4.
  • annular gaps 10 are between the inner wall of the holes provided in the support walls 6 and the lateral surface of the tubes 4 of the cooler 3 passed through these holes in the suction area of the Radiator 3 is larger than in the rest of the radiator.
  • FIGS. 4 and 5 show that the annular gap 10a formed between the tubes 4 and the support wall 6 adjacent to the suction port 8 is larger than the corresponding annular gap 10b in the support wall 6, which is adjacent to the tube sheet 5b.
  • either the size of the annular gaps 10 with the same number of annular gaps 10 per support wall 6 from the support walls 6 on the coolant outlet side to the support walls 6 on the coolant inlet side can be used gain or the number of enlarged annular gaps 10 per support wall 6 increases from the support walls 6 on the cooling water outlet side to the support walls 6 on the cooling water inlet side.
  • an additional supporting wall 11 can be arranged, which is shown in FIG. 3 is drawn.
  • a baffle 12 which runs parallel to the tubes 4 of the cooler 3 and which forms a type of baffle for the steam-gas mixture coming from this first field of the cooler 3.
  • the normal flow direction of the steam D and the non-condensable gases G within the cooler 3 is indicated by arrows in FIG. 3.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Details Of Heat-Exchange And Heat-Transfer (AREA)

Claims (6)

  1. Condenseur de vapeur comportant au moins un faisceau de tubes traversés par de l'eau de refroidissement, dont les tubes sont fixés à leurs extrémités dans des plateaux à tubes et sont soutenus sur leur longueur par plusieurs cloisons de soutien, des passages annulaires entre la surface externe des tubes et la paroi interne des trous résultant du passage des tubes dans les cloisons de soutien, et auquel est associé un refroidisseur destiné aux gaz non condensables et dont les tubes sont séparés des tubes sus-jacents par au moins un volet, les gaz non condensables, notamment l'air, étant aspirés par l'intermédiaire d'une buse d'aspiration (8) hors de l'espace formé par le volet exclusivement à proximité du plateau à tubes situé du côté de l'arrivée de l'eau de refroidissement,
       caractérisé en ce que
       les passages annulaires (10) entre la paroi interne des trous prévus dans les cloisons de soutien (6) et la surface externe des tubes (4) du refroidisseur (3) qui passent à travers ces trous sont réalisés plus grands dans la zone d'aspiration du refroidisseur (3) que dans le reste du refroidisseur (3).
  2. Condenseur de vapeur selon la revendication 1, caractérisé en ce que la surface des passages annulaires (10) situés dans le domaine du refroidisseur (3) augmente depuis les cloisons de soutien (6) situées côté évacuation de l'eau de refroidissement vers les cloisons de soutien (6) situées côté arrivée de l'eau de refroidissement.
  3. Condenseur de vapeur selon la revendication 2, caractérisé en ce que la taille des passages annulaires (10), le nombre de passages annulaires (10) par cloison de soutien (6) étant constant, est agrandie depuis les cloisons de soutien (6) situées côté évacuation de l'eau de refroidissement vers les cloisons de soutien (6) situées côté arrivée de l'eau de refroidissement.
  4. Condenseur de vapeur selon la revendication 2, caractérisé en ce que le nombre de passages annulaires (10) agrandis par cloison de soutien (6) augmente depuis les cloisons de soutien (6) situées côté évacuation de l'eau de refroidissement vers les cloisons de soutien (6) situées côté arrivée de l'eau de refroidissement.
  5. Condenseur de vapeur selon au moins l'une des revendications 1 à 4, caractérisé en ce qu'une cloison de soutien supplémentaire (11) destinée à une partie des tubes du refroidisseur (4) est disposée à proximité de l'orifice de la buse d'aspiration (8).
  6. Condenseur de vapeur selon au moins une des revendications 1 à 5, caractérisé en ce qu'un déflecteur (12) parallèle aux tubes du refroidisseur (4), qui s'étend au-dessus d'une partie de la longueur des tubes du refroidisseur (4) et qui est fixé au volet (7), est disposé à proximité de l'orifice de la buse d'aspiration (8).
EP19920118798 1991-12-13 1992-11-03 Condenseur à vapeur Expired - Lifetime EP0546315B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19914141132 DE4141132C2 (de) 1991-12-13 1991-12-13 Dampfkondensator
DE4141132 1991-12-13

Publications (2)

Publication Number Publication Date
EP0546315A1 EP0546315A1 (fr) 1993-06-16
EP0546315B1 true EP0546315B1 (fr) 1995-03-29

Family

ID=6446974

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19920118798 Expired - Lifetime EP0546315B1 (fr) 1991-12-13 1992-11-03 Condenseur à vapeur

Country Status (3)

Country Link
EP (1) EP0546315B1 (fr)
DE (1) DE4141132C2 (fr)
ES (1) ES2071406T3 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19604704C1 (de) * 1996-02-09 1997-03-06 Balcke Duerr Gmbh Dampfkondensator
EP0976998A1 (fr) * 1998-07-30 2000-02-02 Asea Brown Boveri AG Condenseur de vapeur
EP1014022A1 (fr) * 1998-12-24 2000-06-28 ABB Alstom Power (Schweiz) AG Condenseur à surface
CN102588018A (zh) * 2012-03-17 2012-07-18 华电电力科学研究院 基于tepee两山峰形管束的火电机组冷端优化方法

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE583927C (de) * 1929-12-09 1933-09-12 Westinghouse Electric & Mfg Co Luftkuehler fuer Kondensatoren mit ringfoermig angeordnetem und durch Zwischenwaende unterstuetztem Rohrbuendel
CH423819A (de) * 1965-01-15 1966-11-15 Bbc Brown Boveri & Cie Kondensationsanlage für Dampfturbinen-Abdampf
CH454931A (de) * 1966-04-01 1968-04-30 Sulzer Ag Wärmeübertrager
US3349841A (en) * 1966-08-04 1967-10-31 Ingersoll Rand Co Air cooler for surface condensers
DE3861964D1 (de) * 1988-01-22 1991-04-11 Asea Brown Boveri Dampfkondensator.

Also Published As

Publication number Publication date
DE4141132C1 (fr) 1993-02-11
DE4141132C2 (de) 1995-06-29
EP0546315A1 (fr) 1993-06-16
ES2071406T3 (es) 1995-06-16

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