EP2345841B1 - Heating area assembly of a steam generator or a heat exchanger - Google Patents
Heating area assembly of a steam generator or a heat exchanger Download PDFInfo
- Publication number
- EP2345841B1 EP2345841B1 EP10189120.8A EP10189120A EP2345841B1 EP 2345841 B1 EP2345841 B1 EP 2345841B1 EP 10189120 A EP10189120 A EP 10189120A EP 2345841 B1 EP2345841 B1 EP 2345841B1
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- Prior art keywords
- heating surface
- pipes
- offset
- heizflächenrohre
- heating
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B5/00—Steam boilers of drum type, i.e. without internal furnace or fire tubes, the boiler body being contacted externally by flue gas
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F22—STEAM GENERATION
- F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
- F22B21/00—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically
- F22B21/22—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from water tubes of form other than straight or substantially straight
- F22B21/24—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from water tubes of form other than straight or substantially straight bent in serpentine or sinuous form
Definitions
- the invention relates to a heating surface arrangement of a steam generator or a heat exchanger, with a plurality of heating surfaces and / or a plurality of Bank lake, which are formed of a plurality of substantially parallel Bank lake having horizontally formed regions and between two horizontally formed regions each having a deflection region, wherein in the horizontally formed areas the Edel vomrohre are bundled arranged to Bank lake screen saun, wherein two contiguous arranged Bank lake trim sau each form a Walker moralennadel.
- the invention is directed to a steam generator and / or heat exchanger comprising a heating surface arrangement.
- the Schundrohre a Bank Jerusalem ganges are arranged in alignment.
- the maximum height of a heating surface package is determined by the best possible cleaning of the heating surface arrangement by sootblowers, good accessibility of Bank lakerohre in case of damage and the simplest possible visual control of the Bank lakeanix when driving.
- the optimum heating surface package height is the essential criterion that results in the number of required lanes between the Edel vomunappen throughout the bundle region of a Walker lakeanssen. If the possible Schutbutzwer not optimally utilized, so usually increases the number of lanes between Bank lakes and when equipping the streets with sootblowers and the number of sootblowers. The height of the steam generator or heat exchanger grows according to the resulting additional lanes. Both a greater height of the steam generator or heat exchanger and an increase in Rußblvesseriere are at considerable additional cost for the Steam generator or the heat exchanger connected. On the other hand, if the possible heating surface package height is exceeded, for example, the sootblowing effect is reduced, as a result of which the valency of a heating surface arrangement is reduced.
- a generic Walker voman extract which has a plurality of Bank of Congresssted Hostodian with a plurality of mutually bundled Bank lake is from the GB 347 547 A known. Between two Thompson vomsky prepared a deflection is formed in each case. In the heating surface passage of a heating surface, the three lower heating surface tubes are arranged at a greater distance from one another than the remaining heating surface tubes arranged in the heating surface passage of this one heating surface. The Schundrohre are arranged crosswise in the deflection.
- the invention is therefore based on the object to provide a Walker vomanix a steam generator or a heat exchanger available, by means of which an improved utilization of the possible Walker vomverseau love allows and at the same time the height of a steam generator or the height of the heat exchanger can be reduced.
- the optimum Schuphilbhold may be, for example, from the height of one or more Bankfestennadeln plus the height of n Schuvidrohre or the height of the m Schuvidrohre the fanned Wien lake screenganges, in this embodiment, a heating surface and / or Wien laked by a Schuvidennadel and n Schuvidrohre or m Schuvidrohre the fanned Wien lake toganges is formed.
- the expressions "n” and “m” preferably stand for any integer numbers ⁇ 1, where "n” and “m” do not have to stand for the same number, but can also indicate a different number.
- a preferred embodiment of the invention provides that between the n Schundrohren a Walker vomomes and the m Schundrohren the same Schuvidin toganges an alley, in particular a Rußbläsergasse is formed.
- an alleyway between the fanned-out heating surface passage it is not necessary to provide an alley in a heating surface needle provided above the fanned-out heating surface passage and an alley in a heating surface needle provided under the fanned-out heating surface passage, so that the number of necessary lanes in a heating surface arrangement can be reduced , which in turn the necessary Schucciversiere and thus the height of the steam generator or the heat exchanger can be reduced.
- the mutually offset mutually offset Wienvidrohre and / or the mutually offset mutually offset Wienvidrohre in the deflection have an equal bending radius.
- the two-sided, in particular the two inner, mutually offset Wienvidrohre are each bent to one side formed, wherein the mutually offset mutually offset Wienvidrohre are formed bent to each opposite sides.
- the innermost Edeldonrohr is at a section formed by the cross-sectional area of the Schuvinrohre a Bank lakenadel bent to the right side, wherein the second most far Schuvinrohr bent out to the left side.
- a Walker moralennadel is formed in the deflection region such that the Edelvidennadel has an inner longitudinal division, which is formed reduced by a longitudinal pitch of a heating surface.
- the inner longitudinal division of a Walker vomennadel corresponds to the distance of the innermost Edel vomrohres or the innermost Bank vomziere two adjacent Schuflächurch Maschinen a Walker dichennadel.
- the inner longitudinal division corresponds usually twice the bending radius of the innermost Edel vomrohres or the innermost Bank lakerohre in the deflection.
- the invention it is possible in this embodiment to reduce the usually provided inner longitudinal pitch of a Walker vomennadel, preferably by a longitudinal pitch of a Schundrohres to reduce the height of a Schundennadel and thus the Schundb can.
- the height of the heating surface needle can preferably be reduced so far that the inner longitudinal division of the heating surface needle corresponds to a longitudinal division of a heating surface.
- a further advantageous embodiment of the invention provides that the number of inside one-sided mutually offset Thompson vomettirohre based on the selected bending radius for the Schundrohr used and the required expansion compensation of Schundrohre.
- the invention relates to a steam generator and / or a heat exchanger comprising a Fieiz lakeix emblem as educated and further developed above.
- Fig. 1 shows a schematic representation of a known from the prior art conventional Schuphilanix a steam generator with a first Schuphile 10 and a second Schuphile 12, which are formed of a plurality of mutually parallel Bank lake 14 in the form of coils.
- the Stud vomrohre 14 have horizontally formed portions 16 and deflection 18, wherein the deflection 18 are provided between each two horizontally formed portions 16.
- the Schuphilrohre 14 are arranged bundled to Schuflächurch saun 20, 22, wherein two adjacently arranged Bankflächurch sau 20, 22 each form a Schuphilennadel 24.
- the heating surface arrangement has five mutually parallel heating surface tubes 14, which are arranged in alignment.
- Bankdome 10, 12 each consist of two Bankdomnadeln 24, from whose height the Schund can assume 26 a Bank laked, 12 results.
- the Schundbeck choir 20, 22 is determined by the value of the longitudinal pitch 28 of the height of Edelflächurchêt 20, 22 and the value of the inner longitudinal pitch 30 of a Schuroisennadel 24.
- the longitudinal pitch 28 of a Walker vomsky choires 20, 22 results from the vertical distance between two superimposed, mutually parallel Bankpsychrohre 14, wherein the longitudinal division 28 is measured in each case from the center of Edelphilrohre 14.
- the inner longitudinal division 30, also measured from the center of the Schuloserohre 14, determined from the distance of two Edelflächurchpaper 20, 22 of a Schuphilennadel 24, wherein usually the inner longitudinal division 30 of a Bank vomennadel 24 twice the bending radius of the innermost Banklorrohres 14 in the deflection 18 a Schuphilennadel 24 corresponds.
- the Schundenburganssenen described below relate to all types of steam generators and heat exchangers, such as may be part of power plants, in particular fossil-fired and preferably coal-fired power plants.
- Fig. 2 shows a first embodiment of a Walker vomanix invention, in which a Bank voman emphaszed by the Schuvinrohre 114 of the Bankvid toganges 120a are arranged split, where n Bank vomyake 114, 134 of Schuflächurchganges 120a one above the Schuviden beganges 120a lying first heating surface 110 and a Schuroisennadel 124 of the first heating surface 110 and M Schuroisrohre 114, 136 are associated with a lying below the Schumati barnganges 120a second heating surface 112 and a Walker vomennadel 124 of the second heating surface 112.
- n stands at this in Fig.
- the Schurenete 126 of the second Schurepes 112a results from the height of the Edeldonennadel 124, which is dependent on the longitudinal pitch 128 of the height of the Schuflächurchêt 120th , 122 and the inner longitudinal division 130 of the heating surface needle 124, and the height of the m Edeldonrohre 114, 136 of the Schure prepared Schwarzet 124, 136 of the fanned Bankdones 120 a and an inner longitudinal division 130th
- FIG. 2 shown embodiment of a Schumacheranix a steam generator or Heat exchanger, it is possible to achieve optimally adapted Schutulebunk 126 and thus a reduction of the steam generator height or a reduction of the heat exchanger height.
- an alley 132 is formed, which may be formed, for example, as Rußbläsergasse.
- FIG. 2 shown Bank Riveranix has a free space 142, within which a further heating surface 110, 112 and another Bank lake 110a, 112a can be arranged.
- the free space 142 represents a reserve, which can be filled in order to achieve a further optimally adapted Bank lake 126, which is for example designed such that a further lane 132 can be saved.
- FIG. 3 and FIG. 4 show sectional views of two, parallel to a wall 40, 240 of the steam generator or heat exchanger juxtaposed Bank perennialnadeln 24, 224th
- Fig. 3 shows a conventional, known from the prior art arrangement of Bank of Schwarzeez 14a, 14b, 14c, 14d, 14e a Bank lakenadel 24 Stud laked 10, 12, wherein the Bank lakerohre 14a, 14b, 14c, 14d, 14e are arranged in a row one above the other.
- Fig. 4 shows a second embodiment of a Walker vomanix invention, in which, in contrast to the in Fig. 3
- the two Schuphilrohre 214a, 214b disposed inside the deflecting region 218 of a Walker morennadel 224 Walker primaes 210, 212 are mutually offset on both sides, wherein the outer Schuphilrohre 214c, 214d, 214e not mutually offset from each other, but in a row one above the other are arranged, wherein the outer Schuphilrohre 214c, 214d, 214e engage around the laterally offset from each other inner Bankmatirohre 214a, 214b u-shaped.
- the mutually offset mutually offset Wienvidrohre 214a, 214b have an equally large bending radius, the inner longitudinal division 230 of the Edel vomennadel 224 is smaller as the inner longitudinal division 30 of in Fig. 3 by reducing the inner longitudinal pitch 230 by a longitudinal pitch 228 such that the overall height of the heating surface needle 224 is reduced by a longitudinal pitch 228 from the overall height of a conventional, as in Fig. 3 shown, heating surface needle 24 is reduced.
- the heating surface tubes 214a, 214b which are arranged offset from one another on both sides, are each designed to be curved to one side, the heating surface tubes 214a, 214b arranged offset from one another on both sides being bent out to opposite sides.
- the heating surface pipe 214a is bent out to the left side, and the heating surface pipe 214b is bent out to the right side.
- the staggered arrangement of the heating surface tubes 214a, 214b causes the Schulose Vietnamese spatula, 214b cross over in one place, so that, in the embodiment shown here, in the second Schuflächurchgang 222 innermost Bankicorohr 214a in the first Schuflächurchgang 220 the 2), so that the heating surface tubes 214a, 214b reverse their position in the first heating surface passage 220 to the second heating surface passage 222.
- FIG. 4 shows another way to minimize the Schulle 214a, 214b a Bank lakeennadel 224 in the deflection 218, depending bent to one side and offset by a longitudinal division 228 again in the respective Schuflächurchgang 220, 222 of Bank lakeennadel 224 are threaded.
- Fig. 5 shows an embodiment in which the in Fig. 2 shown first possible embodiment with the in Fig. 4 the second possible embodiment shown is combined in a Schundanix provided.
- the heating surface arrangement shown has two Walker vomune 310a, 312a, which are formed of a plurality of substantially mutually parallel Bank lake 314a, 314b, 314c, 314d, 314e, 314f, 314g, 314h, 314i, 314j, which horizontally formed areas 316 and between two horizontally formed areas 316 each have a deflection region 318, wherein in the horizontally formed regions 316, the Edel vomrohre 314a, 314b, 314c, 314d, 314e, 314f, 314g, 314h, 314i, 314j are arranged bundled to Bankflächurch Spotifyn 320, 322, wherein two adjacent to each other arranged Bankflächurch sau 320, 322 each form a Bank lakenadel 324.
- a Schund malgang 320a is fanned out, wherein n Bankmatirohre 334 of the Bankmati toganges 320a a first heating surface 310 or a first Schuroisennadel 324 of the first heating surface 310 and M Schuroisrohre 336 of the first Schumati toganges 320a a second heating surface 312 or a second Schuroisennadel 324 of the second heating surface are assigned ,
- the two heating surface tubes 314a, 314b lying in each case in the deflection regions 318 are arranged so that they cross each other, offset from one another on both sides, wherein the heating surface tubes 314c, 314d, which lie in the deflection region 318, 314e, 314f, 314g, 314h, 314i, 314j engage around the inner heating surface tubes 314a, 314b arranged on both sides or offset from one another.
- the heating surface package height 326 is determined by the longitudinal pitch 328 of the height of the heating surface passageways 320, 322 of the inner longitudinal division 330 of the heating surface needle 324, the height of the fanned heating surface passageway 334, 336, and the inner longitudinal divider 330 of the diverter. Between the n Edel michangerohren 334 of the fanned Thompson vomit malganges 320 a and the m Wien vom Vietnamese vinegar can be formed. Furthermore, the heating surface arrangement has a free space 342 within which a further heating surface 310, 312 or a further heating surface package 310a, 312a can be provided.
- Fig. 6 shows a known from the prior art unilateral deflection of Bankdom Zelle 14 a Walker lakewovenes 10. Due to the unilateral bending out n all Bankmatirohre 14 a Bank lake toganges 20, 22 and simultaneous jump to all n divisions is a reduction in Bankrochhehe 26 and thus reducing the height of the The disadvantage here is that in the first Schuflächurchgang 20 a Schuroisennadel 24 hot lying Schuroisrohr 14 even after the deflection in the second Schuflächurchgang 22 the hot lying Schulorrohr 14 forms. The coldest Schulorrohr 14 in the first Schuharm screengang 20 also forms the coldest Schumatirohr 14 in the second Schumatita
- Fig. 7 shows a third possible embodiment of the Bank of Congress 424 and thus the Bank whyhehe 426 compared to in Fig. 4 is further reduced by the inner longitudinal pitch 430 of Bankmatiennadel 424 is reduced so that it corresponds to the dimensions of a longitudinal pitch 428 of Bankmatide 410, 412.
- the heating surface needle 424 has two heating surface passages 420, 422, which are formed by ten mutually parallel Bankdonrohre 414a, 414b, 414c, 414d, 414e, 414f, 414g, 414h, 414i, 414j with horizontally formed portions 416 and a deflection 418 , wherein the inner Thompson vomrohre 414a-414d are arranged on one side offset from one another and the outer Schuvinrohre 414e-414j are arranged in series übere each other and surround the inner Bank inhabitrohre 414a-414d U-shaped.
- the inner Edel vomtule 414a-414d are offset from one another in such a way that they cross over 424 in the deflection of the Edelvidennadel.
- the heating surface tube 414j in the first heating surface passage 420 is the least heated heating surface tube and the second heating surface passage 422 is the most heated heating surface tube.
- the difference in heat absorption in the first Schumati gutgang 420 and the second Schuflächurchgang 422 thus resembles in contrast to in Fig. 6 shown, known from the prior art Schuphilanix, largely from.
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Description
Die Erfindung betrifft eine Heizflächenanordnung eines Dampferzeugers oder eines Wärmetauschers, mit mehreren Heizflächen und/oder mehreren Heizflächenpaketen, welche aus mehreren im Wesentlichen parallel zueinander verlaufenden Heizflächenrohren ausgebildet sind, welche horizontal ausgebildete Bereiche und zwischen zwei horizontal ausgebildeten Bereichen jeweils einen Umlenkbereich aufweisen, wobei in den horizontal ausgebildeten Bereichen die Heizflächenrohre zu Heizflächendurchgängen gebündelt angeordnet sind, wobei zwei aneinander angrenzend angeordnete Heizflächendurchgänge jeweils eine Heizflächennadel ausbilden.The invention relates to a heating surface arrangement of a steam generator or a heat exchanger, with a plurality of heating surfaces and / or a plurality of Heizflächenpaketen, which are formed of a plurality of substantially parallel Heizflächenrohren having horizontally formed regions and between two horizontally formed regions each having a deflection region, wherein in the horizontally formed areas the Heizflächenrohre are bundled arranged to Heizflächendurchgängen, wherein two contiguous arranged Heizflächendurchgänge each form a Heizflächenennadel.
Weiterhin richtet sich die Erfindung auf einen Dampferzeuger und/oder Wärmetauscher umfassend eine Heizflächenanordnung.Furthermore, the invention is directed to a steam generator and / or heat exchanger comprising a heating surface arrangement.
Dampferzeuger von Kraftwerken, Heizwerken, Wirbelschichtanlagen und/oder Müllverbrennungsanlagen, welche mit Kohlenstaub, Gas oder Öl und anderen Brennstoffen befeuert werden, weisen in einem Dampferzeuger bzw. Wärmetauscher u. a. oberhalb einer Brennkammer bzw. nachgeschaltet aus Rohrbündeln gebildete Heizflächen auf, welche von Medien, wie Wasser oder Dampf, durchströmt werden, um die Wärme des in der Brennkammer des Dampferzeugers verbrannten Brennstoffs aufzunehmen und abzutransportieren.Steam generators of power plants, heating plants, fluidized bed plants and / or waste incineration plants, which are fired with coal dust, gas or oil and other fuels, have in a steam generator or heat exchanger u. a. above a combustion chamber or downstream of tube bundles formed heating surfaces, which are flowed through by media such as water or steam, to absorb the heat of burned in the combustion chamber of the steam generator fuel and transported away.
Die als Konvektionsheizflächen ausgebildeten Heizflächen einer Heizflächenanordnung bestehen in der Regel aus mehreren unterschiedlich gestalteten Bündelheizflächen, deren Schaltung und Anordnung sich entsprechend der Verfahrensanforderungen aus dem Mediumskreislauf, insbesondere einem Wasserdampfkreislauf, ergibt. Je nach der Höhe einer Heizfläche und der maximalen Höhe eines Heizflächenpaketes werden einzelne oder mehrere Heizflächendurchgänge einer Heizfläche üblicherweise zu einem Heizflächenpaket zusammengefasst, wobei die parallel zueinander verlaufenden Heizflächenrohre horizontal ausgebildete Bereiche und sich daran anschließende Umlenkbereiche aufweisen, um eine schlangenförmige Anordnung der Heizflächenrohre zu erreichen, wobei in den horizontal ausgebildeten Bereichen die Heizflächenrohre zu Heizflächendurchgängen gebündelt angeordnet sind, wobei zwei übereinander angeordnete Heizflächendurchgänge eine Heizflächennadel ausbilden. Die Heizflächenrohre eines Heizflächendurchganges sind dabei fluchtend angeordnet. Die maximale Höhe eines Heizflächenpaketes bestimmt sich nach einer möglichst optimalen Abreinigung der Heizflächenanordnung durch Rußbläser, einer guten Erreichbarkeit der Heizflächenrohre im Schadensfall und einer möglichst einfachen visuellen Kontrolle der Heizflächenanordnung bei Befahrungen.The designed as Konvektionsheizflächen heating surfaces of a Heizflächenanordnung consist usually of several differently shaped bundle heating, their circuit and arrangement according to the process requirements from the medium circuit, in particular a Steam cycle, results. Depending on the height of a heating surface and the maximum height of a Heizflächenpaketes single or more Heizflächurchgänge a heating surface are usually combined to form a Heizflächenpaket, the mutually parallel Heizflächenrohre have horizontally formed areas and adjoining deflection areas to achieve a serpentine arrangement of Heizflächenrohre, wherein in the horizontally formed areas, the Heizflächenrohre are arranged bundled to Heizflächurchgängen, wherein two superposed Heizflächurchgänge form a Heizflächenennadel. The Heizflächenrohre a Heizflächendurchganges are arranged in alignment. The maximum height of a heating surface package is determined by the best possible cleaning of the heating surface arrangement by sootblowers, good accessibility of Heizflächenrohre in case of damage and the simplest possible visual control of the Heizflächenanordnung when driving.
Die optimale Heizflächenpakethöhe ist das wesentliche Kriterium, aus dem sich die Anzahl der erforderlichen Gassen zwischen den Heizflächenpaketen im gesamten Bündelbereich einer Heizflächenanordnung ergeben. Wird die mögliche Heizflächenpakethöhe nicht optimal ausgenutzt, so erhöht sich in der Regel die Anzahl der Gassen zwischen den Heizflächenpaketen und bei Bestückung der Gassen mit Rußbläsern auch die Anzahl der Rußbläser. Die Höhe des Dampferzeugers bzw. Wärmetauschers wächst entsprechend der sich ergebenden zusätzlichen Gassen. Sowohl eine größere Höhe des Dampferzeugers bzw. Wärmetauschers als auch eine Erhöhung der Rußbläserzahl sind mit erheblichen Mehrkosten für den Dampferzeuger bzw. den Wärmetauscher verbunden. Wird die mögliche Heizflächenpakethöhe hingegen überschritten, so verringert sich zum Beispiel die Rußbläserwirkung, wodurch die Wertigkeit einer Heizflächenanordnung reduziert wird.The optimum heating surface package height is the essential criterion that results in the number of required lanes between the Heizflächenpaketen throughout the bundle region of a Heizflächenanordnung. If the possible Heizflächenpakethöhe not optimally utilized, so usually increases the number of lanes between Heizflächenpaketen and when equipping the streets with sootblowers and the number of sootblowers. The height of the steam generator or heat exchanger grows according to the resulting additional lanes. Both a greater height of the steam generator or heat exchanger and an increase in Rußbläserzahl are at considerable additional cost for the Steam generator or the heat exchanger connected. On the other hand, if the possible heating surface package height is exceeded, for example, the sootblowing effect is reduced, as a result of which the valency of a heating surface arrangement is reduced.
Konventionelle Heizflächenanordnungen haben üblicherweise eine Heizflächenpakethöhe, welche aus n Heizflächendurchgängen gebildet wird, wobei die Heizflächenpakethöhe durch die erforderliche Anzahl an inneren Längsteilungen zwischen den Heizflächendurchgängen im Wesentlichen von der Höhe eines Heizflächendurchganges und/oder der Anzahl der Heizflächennadeln in einem Heizflächenpaket und/oder der Höhe der inneren Längsteilung einer Heizflächennadel abhängig ist. Dabei tritt häufig die Situation ein, dass die mögliche Heizflächenpakethöhe nicht ausgenutzt oder überschritten wird, wodurch sich die zuvor aufgeführten Nachteile ergeben.Conventional heating surface arrangements usually have a Heizflächenpakethöhe, which is formed from n Heizflächurchgängen, wherein the Heizflächenpakethöhehe by the required number of inner longitudinal divisions between the Heizflächurchgängen substantially from the height of a Heizflächurchganges and / or the number of Heizflächennadeln in a Heizflächenpaket and / or the height of the inner longitudinal division of a Heizflächenennadel is dependent. The situation often occurs that the possible Heizflächenpakethöhe not exploited or exceeded, resulting in the disadvantages listed above.
Eine gattungsgemäße Heizflächenanordnung, welche mehrere Heizflächendurchgänge mit mehreren gebündelt zueinander angeordneten Heizflächenrohren aufweist ist aus der
Der Erfindung liegt daher die Aufgabe zugrunde, eine Heizflächenanordnung eines Dampferzeugers oder eines Wärmetauschers zur Verfügung zu stellen, mittels welcher eine verbesserte Ausnutzung der möglichen Heizflächenpakethöhe ermöglicht wird und gleichzeitig die Höhe eines Dampferzeugers oder die Höhe des Wärmetauschers reduziert werden kann.The invention is therefore based on the object to provide a Heizflächenanordnung a steam generator or a heat exchanger available, by means of which an improved utilization of the possible Heizflächenpakethöhe allows and at the same time the height of a steam generator or the height of the heat exchanger can be reduced.
Bei einer Heizflächenanordnung der eingangs näher bezeichneten Art wird diese Aufgabe erfindungsgemäß dadurch gelöst, dass ein Heizflächendurchgang aufgefächert ausgebildet ist, wobei n Heizflächenrohre dieses aufgefächerten Heizflächendurchganges einer oberhalb des aufgefächerten Heizflächendurchgangs gelegenen ersten Heizfläche der mehreren Heizflächen oder einer ersten Heizflächennadel der mehreren Heizflächennadeln und m Heizflächenrohre des gleichen Heizflächendurchganges einer unterhalb des aufgefächerten Heizflächendurchgangs gelegenen zweiten Heizfläche der mehreren Heizflächen oder einer zweiten Heizflächennadel der mehreren Heizflächennadeln zugeordnet sind, und/oder, dass zumindest die beiden in einem Umlenkbereich innen liegenden beidseitig versetzt zueinander und/oder zumindest die beiden in einem Umlenkbereich innen liegenden Heizflächenrohre einseitig versetzt zueinander angeordnet sind, wobei die jeweils in dem Umlenkbereich außen liegenden Heizflächenrohre in einer Reihe übereinander angeordnet sind und zumindest ein in dem Umlenkbereich außen liegendes Heizflächenrohr die beidseitig versetzt zueinander angeordneten innen liegenden Heizflächenrohre oder die einseitig versetzt zueinander angeordneten innen liegenden Heizflächenrohre umgreift.In a Heizflächenanordnung of the type described in more detail, this object is achieved in that a Heizflächendurchgang is fanned out, wherein n Heizflächenrohre this fanned Heizflächendurchganges located above the fanned Heizflächendurchgangs first heating surface of the plurality of heating surfaces or a first Heizflächenennadel the more Heizflächennadeln and m Heizflächenrohre the the same Heizflächendurchganges a located below the fanned Heizflächendurchgangs second heating surface of the plurality of heating surfaces or a second Heizflächenennadel the plurality Heizflächenennadeln are assigned, and / or that at least the two in a deflection inside lying on both sides offset from each other and / or at least the two in a deflection inside Heizflächenrohre are arranged on one side offset from one another, wherein each in the deflection outside Hei zflächenrohre are arranged one above the other in a row and at least one in the deflection outside lying Heizflächenrohr the mutually offset from each other arranged inside Heizflächenrohre or unilaterally offset from each other arranged inner Heizflächenrohre surrounds.
Ebenso wird die vorstehende Aufgabe durch einen Dampferzeuger und/oder Wärmetauscher gelöst, der eine wie vorstehend aus- und weitergebildeten Heizflächenanordnung nach einem der Ansprüche 1-7 umfasst.Likewise, the above object is achieved by a steam generator and / or heat exchanger comprising a heating surface arrangement according to any one of claims 1-7, as defined above and further developed.
Durch die aufgefächerte Ausbildung eines Heizflächendurchganges einer Heizflächenanordnung und/oder die seitlich versetzt zueinander angeordnete Anordnung zumindest zweier in einem Umlenkbereich innen liegender Heizflächenrohre ist es möglich, eine zur Verfügung stehende Heizflächenpakethöhe optimal auszunutzen und dabei gleichzeitig die notwendige Bauhöhe des Dampferzeugers bzw. des Wärmetauschers zu minimieren.Due to the fanned out formation of a Heizflächendurchganges a Heizflächenanordnung and / or the laterally offset arrangement of at least two lying in a deflection inside Heizflächenrohre it is possible to optimally utilize an available Heizflächenpakethöhe while minimizing the necessary height of the steam generator and the heat exchanger ,
Bei der aufgefächerten Ausbildung eines Heizflächendurchganges werden n Heizflächenrohre des Heizflächendurchganges einer oberhalb des aufgefächerten Heizflächendurchganges angeordneten ersten Heizfläche oder ersten Heizflächennadel und m Heizflächenrohre des Heizflächendurchganges einer unterhalb des aufgefächerten Heizflächendurchganges angeordneten zweiten Heizfläche oder zweiten Heizflächennadel zugeordnet, wobei der aufgefächerte Heizflächendurchgang bevorzugt im Gesamten aus m+n Heizflächenrohren besteht. Mittels der Auffächerung eines Heizflächendurchganges der Heizflächenanordnung kann jede beliebige Heizflächenpakethöhe realisiert werden, die Anzahl der Gassen zwischen den Heizflächendurchgängen der Heizflächenanordnung minimiert und somit die Bauhöhe des Dampferzeugers bzw. Wärmetauschers reduziert werden. Die optimale Heizflächenpakethöhe kann sich dabei beispielsweise aus der Höhe einer oder mehrerer Heizflächennadeln plus der Höhe der n Heizflächenrohre oder der Höhe der m Heizflächenrohre des aufgefächerten Heizflächendurchganges ergeben, wobei bei dieser Ausgestaltung eine Heizfläche und/oder ein Heizflächenpaket durch eine Heizflächennadel und n Heizflächenrohre oder m Heizflächenrohre des aufgefächerten Heizflächendurchganges ausgebildet ist. Die Ausdrücke "n" und "m" stehen hierbei vorzugsweise für beliebige ganze Zahlen ≥ 1, wobei "n" und "m" nicht für die gleiche Zahl stehen müssen, sondern auch eine unterschiedliche Zahl angeben können.In the fanned-out formation of a Heizflächendurchganges n Heizflächenrohre the Heizflächendurchganges a arranged above the fanned Heizflächendurchganges first heating surface or first Heizflächenennadel and m Heizflächenrohre the Heizflächendurchganges a arranged below the fanned Heizflächendurchganges second heating surface or second Heizflächenennadel be assigned to the fanned Heizflächendurchgang preferably in the whole of m + n Heizflächenrohren exists. By means of the fanning out of a heating surface passage of the heating surface arrangement, any heating surface package height can be realized, the number of lanes between the heating surface passages of the heating surface arrangement can be minimized and thus the overall height of the steam generator or heat exchanger can be reduced. The optimum Heizflächenpakethöhe may be, for example, from the height of one or more Heizflächenennadeln plus the height of n Heizflächenrohre or the height of the m Heizflächenrohre the fanned Heizflächendurchganges, in this embodiment, a heating surface and / or Heizflächenpaket by a Heizflächenennadel and n Heizflächenrohre or m Heizflächenrohre the fanned Heizflächendurchganges is formed. The expressions "n" and "m" preferably stand for any integer numbers ≥ 1, where "n" and "m" do not have to stand for the same number, but can also indicate a different number.
Eine optimale Ausnutzung der möglichen Heizflächenpakethöhe und eine gleichzeitige Reduzierung der Höhe des Dampferzeugers bzw. Wärmetauschers ist alternativ oder gleichzeitig durch eine seitlich, insbesondere beidseitig, versetzt zueinander ausgebildete Anordnung zumindest der beiden am weitesten innen liegenden Heizflächenrohre im Umlenkbereich möglich, wobei vorzugsweise der vertikale Abstand der Heizflächenrohre der inneren Umlenkung einer Heizflächennadel um eine Längsteilung reduziert ist. Die inneren beiden Heizflächenrohre einer Heizflächennadel sind dabei im Umlenkbereich der Heizflächennadel beidseitig versetzt zueinander angeordnet, wobei sich die beidseitig versetzt zueinander angeordneten Heizflächenrohre sich im Umlenkbereich vorzugweise überkreuzen. Durch eine beidseitige versetzte Anordnung der beiden am weitesten innen liegenden Heizflächenrohre im Umlenkbereich ist eine kompaktere Ausbildung einer Heizflächennadel, insbesondere bezüglich ihrer Höhe, möglich, wodurch die Heizflächenpakethöhe und damit die Höhe des Dampferzeugers bzw. Wärmetauschers reduziert werden kann. Des Weiteren ist es auch möglich, mehrere innen liegende Heizflächenrohre einseitig versetzt anzuordnen. Das am weitesten außen liegende Heizflächenrohr oder auch mehrere außen liegende Heizflächenrohre sind dabei im Umlenkbereich derart angeordnet, dass sie die einseitig versetzt zueinander angeordneten innen liegenden Heizflächenrohre, vorzugsweise u-förmig, umgreifen, wobei der vertikale Abstand der Heizflächenrohre der inneren Umlenkung auf die Längsteilung in der Heizflächennadel oder im Heizflächenpaket reduziert werden kann. Durch die einseitige Ausbiegung nur der inneren Heizflächenrohre einer Heizflächennadel ist es möglich, zu erreichen, dass von den äußeren nicht ausgebogenen Heizflächenrohren ein in einem ersten Heizflächendurchgang einer Heizflächennadel am stärksten beheiztes Heizflächenrohr nach der Umlenkung im Umlenkbereich in einem zweiten Heizflächendurchgang ein am wenigsten stark beheiztes Heizflächenrohr der gebündelt angeordneten Heizflächenrohre darstellt und dass ein eher kaltes Heizflächenrohr von den äußeren, nicht ausgebogenen Heizflächenrohren des ersten Heizflächendurchganges in dem zweiten Heizflächendurchgang in einem heißeren Bereich liegt. Dadurch ist eine gleichmäßige, optimierte Wärmeaufnahme über den gesamten Bereich der Heizflächenanordnung erreichbar. Würden hingegen alle Heizflächenrohre im Umlenkbereich einseitig versetzt zueinander angeordnet sein und somit auch das am weitesten außen liegende Heizflächenrohr, so würde das in einem ersten Heizflächendurchgang einer Heizflächennadel heiß liegende Heizflächenrohr auch nach der Umlenkung im Umlenkbereich in einem zweiten Heizflächendurchgang das heiß liegende Heizflächenrohr bilden und das kälteste Heizflächenrohr im ersten Heizflächendurchgang würde ebenfalls das kälteste Heizflächenrohr im zweiten Heizflächendurchgang bilden, wodurch eine wesentlich ungleichmäßigere Wärmeaufnahme über die Heizflächenrohre der Heizflächenordnung gegenüber der erfindungsgemäßen Heizflächenanordnung gegeben ist. Die Anzahl der innen liegenden, einseitig versetzt angeordneten Heizflächenrohre im Umlenkbereich ergibt sich vorzugsweise aus dem gewählten Biegeradius für das eingesetzte Heizflächenrohr und der erforderlichen Dehnungskompensation der Heizflächenrohre.An optimal utilization of the possible Heizflächenpakethöhe and a simultaneous reduction in the height of the steam generator or heat exchanger is alternatively or simultaneously by a laterally, in particular on both sides, offset from each other arrangement of at least the two innermost Heizflächenrohre in the deflection possible, preferably the vertical distance of Heizflächenrohre the inner deflection of a Heizflächenennadel is reduced by a longitudinal pitch. The inner two Heizflächenrohre a Heizflächenennadel are in the deflection of Heizflächenennadel mutually offset from each other, with the mutually offset mutually offset Heizflächenrohre cross over preferably in the deflection. By a two-sided staggered arrangement of the two innermost Heizflächenrohre in the deflection is a more compact design of Heizflächenennadel, in particular with respect to their height, possible, whereby the Heizflächenpakethöhe and thus the height of the steam generator or heat exchanger can be reduced. Furthermore, it is also possible to arrange a plurality of internal Heizflächenrohre unilaterally offset. The outermost Heizflächenrohr or even more outer Heizflächenrohre are arranged in the deflection such that they surround the one-sided offset from each other arranged inside Heizflächenrohre, preferably U-shaped, the vertical distance of the Heizflächenrohre the inner deflection can be reduced to the longitudinal pitch in the Heizflächenennadel or Heizflächenpaket. Due to the one-sided deflection of only the inner Heizflächenrohre a Heizflächenennadel it is possible to achieve that of the outer non-curved Heizflächenrohren a in a first Heizflächendurchgang a Heizflächenennadel the most heated Heizflächenrohr after the deflection in the deflection in a second Heizflächendurchgang least heated Heizflächenrohr represents the bundled disposed Heizflächenrohre and that a rather cold Heizflächenrohr from the outer, not curved Heizflächenrohren the first Heizflächendurchganges in the second Heizflächendurchgang is in a hotter area. This achieves uniform, optimized heat absorption over the entire area of the heating surface arrangement. If, on the other hand, all heating surface tubes in the deflecting region were offset from each other on one side and thus also the outermost heating surface tube, then the heating surface tube located in a first heating surface passage of a heating surface needle would form the heating surface tube lying hot in a second heating surface passage even after the deflection in the deflection region The coldest Heizflächenrohr in the first Heizflächendurchgang would also form the coldest Heizflächenrohr in the second Heizflächendurchgang, creating a much more uneven heat absorption over the Heizflächenrohre the Heizflächenordnung is given to the Heizflächenanordnung invention. The number of internal, one-sided staggered Heizflächenrohre in the deflection preferably results from the selected bending radius for the Heizflächenrohr used and the required expansion compensation of Heizflächenrohre.
Vorteilhafte Ausgestaltungen der Erfindung sind in den Unteransprüchen angegeben.
Eine bevorzugte Ausgestaltung der Erfindung sieht vor, dass zwischen den n Heizflächenrohren eines Heizflächendurchganges und den m Heizflächenrohren des gleichen Heizflächendurchganges eine Gasse, insbesondere eine Rußbläsergasse, ausgebildet ist. Durch die Ausbildung einer Gasse zwischen dem aufgefächerten Heizflächendurchgang, ist es nicht notwendig eine Gasse in einer über dem aufgefächerten Heizflächendurchgang vorgesehenen Heizflächennadel und eine Gasse in einer unter dem aufgefächerten Heizflächendurchgang vorgesehenen Heizflächennadel vorzusehen, so dass die Anzahl der notwendigen Gassen in einer Heizflächenanordnung reduziert werden kann, wodurch wiederum die notwendige Heizflächenpakethöhe und damit die Bauhöhe des Dampferzeugers bzw. des Wärmetauschers reduziert werden kann.Advantageous embodiments of the invention are specified in the subclaims.
A preferred embodiment of the invention provides that between the n Heizflächenrohren a Heizflächendurchganges and the m Heizflächenrohren the same Heizflächendurchganges an alley, in particular a Rußbläsergasse is formed. By forming an alleyway between the fanned-out heating surface passage, it is not necessary to provide an alley in a heating surface needle provided above the fanned-out heating surface passage and an alley in a heating surface needle provided under the fanned-out heating surface passage, so that the number of necessary lanes in a heating surface arrangement can be reduced , which in turn the necessary Heizflächenpakethöhe and thus the height of the steam generator or the heat exchanger can be reduced.
Weiter ist es bevorzugt vorgesehen, dass die beidseitig versetzt zueinander angeordneten Heizflächenrohre und/oder die einseitig versetzt zueinander angeordneten Heizflächenrohre in dem Umlenkbereich einen gleich großen Biegeradius aufweisen. Hierdurch kann die Packungsdichte der Heizflächenrohre einer Heizflächennadel im Umlenkbereich und damit in der gesamten Heizflächennadel erhöht werden, wodurch die notwendige Heizflächenpakethöhe reduziert werden kann.Furthermore, it is preferably provided that the mutually offset mutually offset Heizflächenrohre and / or the mutually offset mutually offset Heizflächenrohre in the deflection have an equal bending radius. As a result, the packing density of Heizflächenrohre a Heizflächenennadel be increased in the deflection and thus in the entire Heizflächenennadel, whereby the necessary Heizflächenpakethöhe can be reduced.
Gemäß einer weiter bevorzugten Ausbildung sind die beidseitig, insbesondere die beiden innen liegenden, versetzt zueinander angeordneten Heizflächenrohre je zu einer Seite ausgebogen ausgebildet, wobei die beidseitig versetzt zueinander angeordneten Heizflächenrohre zu sich jeweils gegenüberliegenden Seiten ausgebogen ausgebildet sind. Beispielsweise ist dabei das am weitesten innen liegende Heizflächenrohr bei einem Schnitt durch die Querschnittsfläche der Heizflächenrohre einer Heizflächennadel zur rechten Seite hin ausgebogen ausgebildet, wobei das zweit weitest innen liegende Heizflächenrohr zur linken Seite hin ausgebogen ausgebildet ist. Dadurch, dass die beidseitig versetzt zueinander angeordneten Heizflächenrohre im Umlenkbereich der Heizflächennadel je zu einer sich gegenüberliegenden Seite ausgebogen ausgebildet sind, kann der für ein Heizflächenrohr erforderliche Biegeradius der beidseitig versetzt zueinander angeordneten Heizflächenrohre im Umlenkbereich unverändert bleiben, bei gleichzeitiger Reduzierung der Höhe der Heizflächennadel und Reduzierung der Bauhöhe des Dampferzeugers bzw. des Wärmetauschers. Die beidseitig versetzt zueinander angeordneten Heizflächenrohre sind vorzugsweise im Umlenkbereich sich überkreuzend, ineinander verschachtelt angeordnet, wodurch eine Erhöhung der Packungsdichte der Heizflächenrohre im Umlenkbereich einer Heizflächennadel erzielt werden kann.According to a further preferred embodiment, the two-sided, in particular the two inner, mutually offset Heizflächenrohre are each bent to one side formed, wherein the mutually offset mutually offset Heizflächenrohre are formed bent to each opposite sides. For example, the innermost Heizflächenrohr is at a section formed by the cross-sectional area of the Heizflächenrohre a Heizflächenennadel bent to the right side, wherein the second most far Heizflächenrohr bent out to the left side. Characterized in that the mutually offset mutually offset Heizflächenrohre in the deflection of the Heizflächenennadel each bent to an opposite side, the required for a Heizflächenrohr bending radius of both sides mutually offset Heizflächenrohre in the deflection can remain unchanged, while reducing the height of Heizflächenennadel and reduction the height of the steam generator or the heat exchanger. The mutually offset mutually offset Heizflächenrohre are preferably in the deflection cross-nested, arranged nested, whereby an increase in the packing density of Heizflächenrohre in the deflection of a Heizflächenennadel can be achieved.
Weiter ist es bevorzugt vorgesehen, dass eine Heizflächennadel in dem Umlenkbereich derart ausgebildet ist, dass die Heizflächennadel eine innere Längsteilung aufweist, welche um eine Längsteilung einer Heizfläche reduziert ausgebildet ist. Die innere Längsteilung einer Heizflächennadel entspricht dem Abstand des am weitesten innen liegenden Heizflächenrohres bzw. der am weitesten innen liegenden Heizflächenrohre zweier aneinander angrenzender Heizflächendurchgänge einer Heizflächennadel. Die innere Längsteilung entspricht üblicherweise zwei Mal dem Biegeradius des am weitesten innen liegenden Heizflächenrohres bzw. der am weitesten innen liegenden Heizflächenrohre im Umlenkbereich. Erfindungsgemäß ist es bei dieser Ausgestaltung möglich, die üblicherweise vorgesehene innere Längsteilung einer Heizflächennadel, vorzugsweise um eine Längsteilung eines Heizflächenrohres, zu reduzieren, um die Höhe einer Heizflächennadel und damit die Heizflächenpakethöhe reduzieren zu können. Die Höhe der Heizflächennadel kann dabei vorzugsweise derart weit reduziert sein, dass die innere Längsteilung der Heizflächennadel einer Längsteilung einer Heizfläche entspricht.Further, it is preferably provided that a Heizflächenennadel is formed in the deflection region such that the Heizflächenennadel has an inner longitudinal division, which is formed reduced by a longitudinal pitch of a heating surface. The inner longitudinal division of a Heizflächenennadel corresponds to the distance of the innermost Heizflächenrohres or the innermost Heizflächenrohre two adjacent Heizflächurchgänge a Heizflächenennadel. The inner longitudinal division corresponds usually twice the bending radius of the innermost Heizflächenrohres or the innermost Heizflächenrohre in the deflection. According to the invention, it is possible in this embodiment to reduce the usually provided inner longitudinal pitch of a Heizflächenennadel, preferably by a longitudinal pitch of a Heizflächenrohres to reduce the height of a Heizflächenennadel and thus the Heizflächenpakethöhe can. The height of the heating surface needle can preferably be reduced so far that the inner longitudinal division of the heating surface needle corresponds to a longitudinal division of a heating surface.
Eine weitere vorteilhafte Ausgestaltung der Erfindung sieht vor, dass die Anzahl der innen liegenden einseitig versetzt zueinander angeordneten Heizflächenrohre auf dem gewählten Biegeradius für das eingesetzte Heizflächenrohr und der erforderlichen Dehnungskompensation der Heizflächenrohre basiert.A further advantageous embodiment of the invention provides that the number of inside one-sided mutually offset Heizflächenrohre based on the selected bending radius for the Heizflächenrohr used and the required expansion compensation of Heizflächenrohre.
Ferner betrifft die Erfindung einen Dampferzeuger und/oder einen Wärmetauscher umfassend eine wie vorstehend aus- und weitergebildete Fieizflächenanordnung.Furthermore, the invention relates to a steam generator and / or a heat exchanger comprising a Fieizflächenanordnung as educated and further developed above.
Nachfolgend wird die Erfindung unter Bezugnahme auf die anliegenden Zeichnungen anhand bevorzugter Ausführungsformen näher erläutert.The invention will be explained in more detail with reference to the accompanying drawings with reference to preferred embodiments.
Es zeigen:
- Fig. 1
- eine schematische Darstellung einer ersten konventionellen Heizflächenanordnung;
- Fig. 2
- eine schematische Darstellung einer erfindungsgemäßen Heizflächenanordnung gemäß einer ersten Ausführungsform mit einem aufgefächerten Heizflächendurchgang;
- Fig. 3
- eine schematische Schnittdarstellung durch die Querschnittsfläche einer zweiten konventionellen Heizflächennadel;
- Fig. 4
- eine schematische Darstellung einer erfindungsgemäßen Heizflächenanordnung gemäß einer zweiten Ausführungsform mit einer Schnittdarstellung durch die Querschnittsfläche einer erfindungsgemäßen Heizflächennadel, welche eine beidseitig versetzte Ausbiegung der beiden innen liegenden Heizflächenrohre aufweist;
- Fig. 5
- eine schematische Darstellung einer erfindungsgemäßen Heizflächenanordnung gemäß einer Kombination der in
Fig. 2 gezeigten ersten und der inFig. 4 gezeigten zweiten Ausführungsform; - Fig. 6
- eine schematische Darstellung einer dritten konventionellen Heizflächenanordnung; und
- Fig. 7
- eine schematische Darstellung einer erfindungsgemäßen Heizflächenanordnung gemäß einer dritten Ausführungsform mit einer einseitigen Ausbiegung mehrerer innen liegender Heizflächenrohre einer Heizflächennadel.
- Fig. 1
- a schematic representation of a first conventional Heizflächenanordnung;
- Fig. 2
- a schematic representation of a Heizflächenanordnung invention according to a first embodiment with a fanned Heizflächendurchgang;
- Fig. 3
- a schematic sectional view through the cross-sectional area of a second conventional Heizflächenennadel;
- Fig. 4
- a schematic representation of a Heizflächenanordnung invention according to a second embodiment with a sectional view through the cross-sectional area of a Heizflächenennadel invention, which has a mutually offset deflection of the two inner Heizflächenrohre;
- Fig. 5
- a schematic representation of a Heizflächenanordnung invention according to a combination of in
Fig. 2 shown first and inFig. 4 shown second embodiment; - Fig. 6
- a schematic representation of a third conventional Heizflächenanordnung; and
- Fig. 7
- a schematic representation of a Heizflächenanordnung invention according to a third embodiment with a one-sided deflection of several internal Heizflächenrohre a Heizflächenennadel.
Bei dem in
Durch die entsprechende Ausnutzung der möglichen Heizflächenpakethöhe 26 ergibt sich die Anzahl der notwendigen Gassen 32 einer Heizflächenanordnung. Mit der Anzahl der notwendigen Gassen 32 erhöht sich jedoch auch die Höhe des Dampferzeugers bzw. Wärmetauschers. Bei einer optimalen Ausnutzung der möglichen Heizflächenpakethöhe 26 kann die Anzahl der notwendigen Gassen 32 und damit auch die Höhe des Dampferzeugers bzw. Wärmetauschers reduziert werden. Eine optimale Ausnutzung der möglichen Heizflächenpakethöhe 26 ist durch die in den
Die nachfolgend beschriebenen Heizflächenanordnungen betreffen alle Arten von Dampferzeugern und Wärmetauschern, wie sie beispielsweise Bestandteil von Kraftwerken, insbesondere fossilbefeuerten und vorzugsweise kohlebefeuerten Kraftwerken, sein können.The Heizflächenanordnungen described below relate to all types of steam generators and heat exchangers, such as may be part of power plants, in particular fossil-fired and preferably coal-fired power plants.
Durch die in
Zwischen den n Heizflächenrohren 114, 134 des Heizflächendurchganges 120a und den m Heizflächenrohren 114, 136 des Heizflächendurchganges 120a ist eine Gasse 132 ausgebildet, die beispielsweise als Rußbläsergasse ausgebildet sein kann.Between the
Durch die Auffächerung eines Heizflächendurchganges 120a kann jede beliebige Heizflächenpakethöhe 126 realisiert, die Anzahl der Gassen 132 minimiert und somit die Dampferzeugerhöhe bzw. Wärmetauscherhöhe reduziert werden.By fanning a Heizflächendurchganges 120 a any
Die in
Zum Erreichen einer optimalen Ausnutzung der möglichen Heizflächenpakethöhe kann es ferner erfindungsgemäß vorgesehen sein, wie in
Die in
Die in
Claims (8)
- Heating surface arrangement of a steam generator or a heat exchanger with multiple heating surfaces (110, 112, 310, 312) and/or multiple heating surface banks (110a, 112a, 210, 212, 310a, 312a, 410, 412), which are configured from multiple heating surface pipes (114, 214a, 214b, 214c, 214d, 214e, 314a, 314b, 314c, 314d, 314e, 314f, 314g, 314h, 314i, 314j, 414a, 414b, 414c, 414d, 414e, 414f, 414g, 414h, 414i, 414j), which run substantially parallel to one another and have horizontally configured regions (116, 216, 316, 416) and a respective deflection region (118, 218, 318, 418) between two horizontally configured regions (116, 216, 316, 416), wherein in the horizontally configured regions (116, 216, 316, 416) the heating surface pipes (114, 214a, 214b, 214c, 214d, 214e, 314a, 314b, 314c, 314d, 314e, 314f, 314g, 314h, 314i, 314j, 414a, 414b, 414c, 414d, 414e, 414f, 414g, 414h, 414i, 414j) are arranged in bundles to form heating surface passages (120,122, 220, 222, 320, 322, 420, 422), wherein two heating surface passages (120,122, 220, 222, 320, 322, 420, 422) arranged to adjoin one another respectively configure a heating surface needle (124, 224, 324, 424), characterised in that
a heating surface passage (120a, 320a) is formed fanned out, wherein n heating surface pipes (134, 334) of this fanned-out heating surface passage (120a, 320a) are associated with a first heating surface (110, 310) of the multiple heating surfaces (110, 112, 310, 312), which is located above the fanned-out heating surface passage (120a, 320a), or with a first heating surface needle (124, 324) of the multiple heating surface needles (124, 224, 324, 424)
and m heating pipes (136, 336) of the same heating surface passage (120a, 320a) are associated with a second heating surface (112, 312) of the multiple heating surfaces (110, 112, 310, 312), which is located below the fanned-out heating surface passage (120a, 320a), or with a second heating surface needle (124, 324) of the multiple heating surface needles (124, 224, 324, 424),
and/or
that at least the two heating surface pipes (214a, 214b, 314a, 314b) located on the inside in a deflection region (318) are offset in relation to one another on both sides and/or at least the two heating surface pipes (414a, 414b, 414c, 414d) located on the inside in a deflection region (418) are offset in relation to one another on one side, wherein the respective heating surface pipes (214c, 214d, 214e, 314c, 314d, 314e, 314f, 314g, 314h, 314i, 314j, 414e, 414f, 414g, 414h, 414i, 414j) located on the outside in the deflection region (218, 318, 418) are arranged in a row one above the other, and
at least one heating surface pipe (214c, 214d, 214e, 314c, 314d, 314e, 314f, 314g, 314h, 314i, 314j, 414e, 414f, 414g, 414h, 414i, 414j) located on the outside in the deflection region (218, 318, 418) encompasses the heating surface pipes (214a, 214b, 314a, 314b), which are located on the inside and are offset in relation to one another on both sides, or the heating surface pipes (414a, 414b, 414c, 414d), which are located on the inside and are offset in relation to one another on one side. - Heating surface arrangement according to claim 1, characterised in that a channel (132, 332), in particular a soot blower channel, is configured between the n heating surface pipes (134, 334) of a heating surface passage (120a, 320a) and the m heating surface pipes (136, 336) of the same heating surface passage (120a, 320a).
- Heating surface arrangement according to claim 1 or 2, characterised in that the heating surface pipes (214a, 214b, 314a, 314b), which are offset in relation to one another on both sides, and/or the heating surface pipes (414a, 414b, 414c, 414d), which are offset in relation to one another on one side, have the same bending radius in the deflection region (218,318,418).
- Heating surface arrangement according to one of claims 1 to 3, characterised in that the heating surface pipes (214a, 214b, 314a, 314b), which are offset in relation to one another on both sides, are each bent outwards to one side, wherein the laterally offset heating surface pipes (214a, 214b, 314a, 314b) are bent outwards to respectively opposite sides.
- Heating surface arrangement according to one of claims 1 to 4, characterised in that a heating surface needle (224, 324) is configured in the deflection region (218, 318) in such a way that the heating surface needle (224, 324) has an internal longitudinal division (230, 330), which is reduced by a longitudinal division (228, 328) of a heating surface (210, 212).
- Heating surface arrangement according to one of claims 1 to 4, characterised in that a heating surface needle (424) is configured in the deflection region (418) in such a way that the heating surface needle (424) has an internal longitudinal division (430), which corresponds to a longitudinal division (428) of a heating surface (410, 412).
- Heating surface arrangement according to one of claims 1 to 6, characterised in that the number of heating surface pipes (214a, 214b, 314a, 314b, 414a, 414b, 414c, 414d), which are located on the inside and are offset in relation to one another on one side, is based on the selected bending radius for the heating surface pipe (214a, 214b, 314a, 314b, 414a, 414b, 414c, 414d) used and the necessary expansion compensation of the heating surface pipes (214a, 214b, 314a, 314b, 414a, 414b, 414c, 414d).
- Steam generator and/or heat exchanger comprising a heating surface arrangement according to one of claims 1 to 7.
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PL10189120T PL2345841T3 (en) | 2009-11-06 | 2010-10-27 | Heating area assembly of a steam generator or a heat exchanger |
SI201031395A SI2345841T1 (en) | 2009-11-06 | 2010-10-27 | Heating area assembly of a steam generator or a heat exchanger |
RS20170223A RS55749B1 (en) | 2009-11-06 | 2010-10-27 | Heating area assembly of a steam generator or a heat exchanger |
HRP20170282TT HRP20170282T1 (en) | 2009-11-06 | 2017-02-20 | Heating area assembly of a steam generator or a heat exchanger |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009052246 | 2009-11-06 | ||
DE102010038978.1A DE102010038978C5 (en) | 2009-11-06 | 2010-08-05 | Heating surface arrangement of a steam generator or a heat exchanger and a steam generator and / or heat exchanger comprising such a heating surface arrangement |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2345841A1 EP2345841A1 (en) | 2011-07-20 |
EP2345841B1 true EP2345841B1 (en) | 2016-12-07 |
Family
ID=44021978
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10189120.8A Revoked EP2345841B1 (en) | 2009-11-06 | 2010-10-27 | Heating area assembly of a steam generator or a heat exchanger |
Country Status (10)
Country | Link |
---|---|
EP (1) | EP2345841B1 (en) |
DE (1) | DE102010038978C5 (en) |
ES (1) | ES2615339T3 (en) |
HR (1) | HRP20170282T1 (en) |
HU (1) | HUE032236T2 (en) |
PL (1) | PL2345841T3 (en) |
PT (1) | PT2345841T (en) |
RS (1) | RS55749B1 (en) |
SI (1) | SI2345841T1 (en) |
ZA (1) | ZA201007941B (en) |
Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB347547A (en) | 1930-07-08 | 1931-04-30 | Schmidt Sche Heissdampf | Improvements in steam generators |
GB846402A (en) | 1957-11-08 | 1960-08-31 | Babcock & Wilcox Ltd | Improvements in tubulous vapour generators |
CH374082A (en) | 1963-03-01 | 1963-12-31 | Sulzer Ag | Arrangement of contact heating surfaces in a steam generator |
DE1401649A1 (en) | 1961-10-25 | 1969-01-23 | Svenska Maskinverken Ab | Heat exchanger consisting of pipes |
DE2041129A1 (en) | 1970-08-19 | 1972-02-24 | Herpen Co Kg La Mont Kessel | Wall cladding for forced-flow water tube boiler |
JPS5977203A (en) | 1982-07-08 | 1984-05-02 | バブコツク日立株式会社 | Steam generator |
NL9402107A (en) | 1994-12-12 | 1996-07-01 | Stork Ketels Bv | Device for generating steam |
US20080282997A1 (en) | 2007-05-17 | 2008-11-20 | Gayheart Jeb W | Economizer arrangement for steam generator |
Family Cites Families (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2033077A (en) * | 1931-04-16 | 1936-03-03 | Babcock & Wilcox Co | Tube support |
GB1117813A (en) * | 1965-02-17 | 1968-06-26 | Babcock & Wilcox Ltd | Improvements in tubulous walls arranged for supporting heat exchange tube banks |
DE1501665A1 (en) * | 1965-03-26 | 1969-08-14 | Vorkauf Heinrich | Pipe element for heat exchanger |
DE4308628C2 (en) * | 1993-03-18 | 1995-06-29 | Erk Eckrohrkessel | Flag heating surface |
DE4344409C2 (en) * | 1993-12-24 | 2002-10-31 | Erk Eckrohrkessel | Steam or hot water generators with flag heating surfaces arranged in the flue gas stream |
-
2010
- 2010-08-05 DE DE102010038978.1A patent/DE102010038978C5/en not_active Expired - Fee Related
- 2010-10-27 RS RS20170223A patent/RS55749B1/en unknown
- 2010-10-27 HU HUE10189120A patent/HUE032236T2/en unknown
- 2010-10-27 EP EP10189120.8A patent/EP2345841B1/en not_active Revoked
- 2010-10-27 PL PL10189120T patent/PL2345841T3/en unknown
- 2010-10-27 PT PT101891208T patent/PT2345841T/en unknown
- 2010-10-27 SI SI201031395A patent/SI2345841T1/en unknown
- 2010-10-27 ES ES10189120.8T patent/ES2615339T3/en active Active
- 2010-11-05 ZA ZA2010/07941A patent/ZA201007941B/en unknown
-
2017
- 2017-02-20 HR HRP20170282TT patent/HRP20170282T1/en unknown
Patent Citations (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB347547A (en) | 1930-07-08 | 1931-04-30 | Schmidt Sche Heissdampf | Improvements in steam generators |
GB846402A (en) | 1957-11-08 | 1960-08-31 | Babcock & Wilcox Ltd | Improvements in tubulous vapour generators |
DE1401649A1 (en) | 1961-10-25 | 1969-01-23 | Svenska Maskinverken Ab | Heat exchanger consisting of pipes |
CH374082A (en) | 1963-03-01 | 1963-12-31 | Sulzer Ag | Arrangement of contact heating surfaces in a steam generator |
DE2041129A1 (en) | 1970-08-19 | 1972-02-24 | Herpen Co Kg La Mont Kessel | Wall cladding for forced-flow water tube boiler |
JPS5977203A (en) | 1982-07-08 | 1984-05-02 | バブコツク日立株式会社 | Steam generator |
NL9402107A (en) | 1994-12-12 | 1996-07-01 | Stork Ketels Bv | Device for generating steam |
US20080282997A1 (en) | 2007-05-17 | 2008-11-20 | Gayheart Jeb W | Economizer arrangement for steam generator |
Also Published As
Publication number | Publication date |
---|---|
HUE032236T2 (en) | 2017-09-28 |
SI2345841T1 (en) | 2017-03-31 |
DE102010038978B8 (en) | 2017-05-04 |
HRP20170282T1 (en) | 2017-04-21 |
DE102010038978B4 (en) | 2017-02-09 |
DE102010038978A1 (en) | 2011-12-15 |
ZA201007941B (en) | 2011-07-27 |
RS55749B1 (en) | 2017-07-31 |
PT2345841T (en) | 2017-03-13 |
ES2615339T3 (en) | 2017-06-06 |
PL2345841T3 (en) | 2017-06-30 |
DE102010038978C5 (en) | 2020-04-09 |
EP2345841A1 (en) | 2011-07-20 |
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