EP1793188A1 - Condenseur à surface - Google Patents

Condenseur à surface Download PDF

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Publication number
EP1793188A1
EP1793188A1 EP05026438A EP05026438A EP1793188A1 EP 1793188 A1 EP1793188 A1 EP 1793188A1 EP 05026438 A EP05026438 A EP 05026438A EP 05026438 A EP05026438 A EP 05026438A EP 1793188 A1 EP1793188 A1 EP 1793188A1
Authority
EP
European Patent Office
Prior art keywords
tubes
condenser
surface condenser
tube
corrugated structure
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.)
Withdrawn
Application number
EP05026438A
Other languages
German (de)
English (en)
Inventor
Ramón Dimas Rodriguez Barrado
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.)
Kelvion Thermal Solutions SA
Original Assignee
GEA Iberica SA
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 GEA Iberica SA filed Critical GEA Iberica SA
Priority to EP05026438A priority Critical patent/EP1793188A1/fr
Publication of EP1793188A1 publication Critical patent/EP1793188A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • 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 present invention relates to a surface condenser of industrial scale, in particular condensers of the type used in conjunction power plants, co-generation plants, turbo-generators in ships and the like.
  • the invention relates to vacuum surface condensers, in which a tube bundle provides a large surface area for condensation of steam on the outer surfaces of the tubes.
  • the object of the present invention is to improve efficiency of such vacuum surface condensers, in particular to improve the heat exchange capacity between steam and the cooling medium within the tubes.
  • Another object of the present invention is to reduce the dimensions and weight of such surface condensers, which conventionally are very large and often difficult to transport and assemble at the plant site.
  • a surface condenser is provided as defined in claim 1.
  • a combined cycle power plant is subject of claim 10.
  • Embodiments of preferred embodiments are defined in the subclaims.
  • the present surface condenser according to claim 1 comprises a shell having water boxes at opposite ends thereof.
  • a tube bundle is supported within the shell and extends between the water boxes, where at least a portion of the individual tubes of the tube bundle are formed with a corrugated structure.
  • the combined cycle power plant according to claim 10 comprises at least a steam generator, a steam turbine and a vacuum surface condenser.
  • the vacuum surface condenser of the combine cycle power plant comprises a shell including water boxes at opposite ends thereof, and a tube bundle disposed within the shell and extending between the water boxes, wherein at least a portion of the individual tubes of the tube bundle are formed with a corrugated structure
  • the corrugated structure of the surface condenser is preferably formed as alternating ridges and grooves on the outer surface as well as the inner surface of the tubes.
  • the present corrugated tubes offer a certain flow resistance to steam passage over the outer surfaces as well as resistance to cooling water passage within the tubes. The resulting turbulence in flow of both steam and water increases thermal efficiency of heat transfer.
  • the increased pressure drop across the heat exchanger in the steam flow as well as in the coolant water caused by the increased flow resistance is not substantial.
  • a condenser with the same thermal power rating can now be constructed with such corrugated tubes, where the dimensions and weight of the condenser is greatly reduced by 20 to 40 %.
  • the thermal capacity can be increased on the order of 30 % or more.
  • the present invention can preferably be used in combined cycle power plants, that are small or medium sized and are used to produce electricity and heat.
  • the vacuum surface condenser according to the present invention has many advantages. One of them is that the vacuum surface condenser can be manufactured on the company area and then be transported on public roads to the location of the combined cycle power plant.
  • Standard he vacuum surface condensers maybe replaced with new vacuum surface condensers. It is possible to upgrade older units to the new design. According to the invention a retubing, refurbishment and replacement is possible while at the same time the efficiency and power is increased.
  • the new one maybe mounted in the factory and transported to the site of the combined cycle power plant.
  • a vacuum surface condenser according to the invention is preferably also used on ships as part of an auxiliary power system on a ship.
  • the use of a vacuum surface condenser with corrugated tubes as described here makes it possible to user shorter condensers. This leaves more space for transporting goods etc. on the ship.
  • Fig. 1 illustrates one embodiment of the present invention, comprising an industrial scale condenser.
  • a tube bundle 7 formed of the plurality of tubes is disposed within a shell 1 of the vacuum surface condenser.
  • Water boxes 2, 3 are located at either end of the tube bundle for supply and discharge of cooling water.
  • Cooling water enters the water box 2 through an inlet 20, where it is directed by a baffle 21 into an upper portion of the tubes 9.
  • water box 3 (to the left in Fig. 1), the cooling water is deflected to return through the lower lying tubes 9 of the tube bundle 7.
  • the cooling water is then discharged from the water box 2 at the outlet 22 and in typical applications will circulate in a closed circuit.
  • the discharged cooling water is commonly sent to a cooling tower or an air fan cooling system in closed circuit operation. Sea water or river water can alternatively be used for cooling, where available.
  • the shell has a length of 4 m and a diameter of 1.48 m.
  • the shell encloses 1100 tubes each having a diameter of 25.4 mm. Cooling water is passed through the upper tubes in one direction, where water is deflected and flows in counter direction for the second pass through the lower tubes.
  • the arrangement of the tubes in sections, with spaces there between, has been found to be particularly efficient for the condensation process.
  • the tubes are preferably formed of refined metal.
  • the material is selected according to the water quality or source.
  • the material may be refined steel.
  • the tubes can be twisted to form the corrugated structure.
  • the term 'corrugated structure' used herein is to be understood as a succession of ridges 11 and grooves 12 as seen in a longitudinal cross section of the tube 9 as shown in Fig. 3.
  • the ridges 11 and grooves 12 can be formed as wrinkles, folds, riffles or the like.
  • the ridges or grooves can run smoothly in a wavelike structure, or they can have peaks and valleys, with edges.
  • the tubes are also preferably of such a material that they can withstand operation with sea water as a cooling medium.
  • the corrugated structure extends substantially over the entire length of the tubes, although it is also possible that the corrugated structure only be provided in certain sections of the axial length of the tubes. Such sections for example would preferably be in the regions within the shell where the flow velocity of the steam is the highest.
  • the corrugations have a pitch P, defined as a distance between successive grooves 12 or between successive ridges 11.
  • the pitch P is uniform along the axial length of the tube, however the pitch may vary from section to section of the tube.
  • the configuration of the ridges and/or grooves shown in Fig. 3 defines a helical pattern, which progresses above the axis of the tube in longitudinal direction.
  • the helical corrugations maybe arranged on the inside of the tube and/or on the outside of the tubes.
  • the helical pattern develops as a right hand or left hand turn along the tube axis. In this embodiment, the turn is continuous in one direction.
  • One advantage is that a cleaning of the inside is accomplished by the streaming cooling medium. When other structures are used small particles can deposit on the inside of the tubes more easily.
  • the self-cleaning effect of this embodiment is achieved by a high level of turbulence and by the helical structure. This reduces a fouling effect.
  • the turn may be not continuous in one direction. It is possible to alternate the turn direction along the length of the tube. It is also contemplated to provide other patterns other than helical. For example, a meandering structure can be achieved by alternating the left hand and right hand turning of the tube during formation.
  • both the inside surface 14 and the outer surface 15 of the tubes comprise ridges 11 and grooves 12, which causes an irregular flow of gas or fluid along the surfaces.
  • cooling water flowing within the tube will create turbulence at the inside surface wall to a certain extent.
  • Such turbulence more thoroughly mixes the cooling water at the inner wall of the tube, which has the result that the heat transfer from the coolant medium to the wall surface is more effective.
  • the corrugated structure In addition to developing turbulence in the respective tube side flow and shell side flow, the corrugated structure also increases the total surface area of the tubes available for heat transfer.
  • the magnitude of the surface area increase will depend upon the dimensions of the grooves 12 and ridges 11. As will be readily understood by the skilled person, with deeper grooves and higher ridges, the total surface area available per unit length of the tube will increase.
  • the tube has a nominal diameter of 25.4 mm.
  • the pitch P in this example is 18 mm.
  • the corrugation depth T in Fig. 3 is 0.7 mm.
  • the depth T is defined as the radial distance from the bottom of a groove 12 on the inside surface 14 of the tube to the top of the ridge 11 on the outer surface 15 of the tube.
  • the corrugation depth T is preferably in a range of 0.5 to 0.9 mm.
  • the diameter of the individual tubes is preferably in the range of 22 to 28 mm.
  • the pitch P of the helical pattern is advantageously in the range of 15 to 21 mm.
  • a condenser dimensioned for a steam flow of 32 t/h at a condensation pressure of 0.068 bar is considered.
  • Sea water is employed as the cooling medium, the inlet/outlet temperatures being 27°/32.5°C.
  • the total length of the conventional condenser could be reduced from 5.6 m to 4.2 m, a reduction of 25 %.
  • the heat exchanger surface is reduced from 715 m 2 to 500 m 2 , a reduction of 30 %.
  • the overall weight of the condenser reduces from 14 t to 11 t, or is 21 % lighter.
  • This condenser unit is designed for a greater steam flow capacity of 320 t/h.
  • the condensation pressure is 0.0456 bar.
  • sea water is used as the cooling medium and the inlet/outlet temperatures are 20.4°/28.1°C.
  • the diameter of the condenser shell is reduced from 5.2 m to 3.6 m, a reduction of 30 %.
  • the heat exchanger surface reduces from 10,100 m 2 to 6,700 m 2 or a reduction of 34 %.
  • the weight of the condenser unit reduces from 270 t to 140 t or is 48 % lighter.
  • the same cooling capacity can be achieved with greatly reduced size and weight of the condenser, which is allowed by the provision of corrugated tubes throughout the entire tube bundle.
  • the reduced size of the condenser has the further advantage of being more economical in manufacture and transportation to the plant site. Installation time and special equipment for handling of the condenser can also be minimized.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP05026438A 2005-12-05 2005-12-05 Condenseur à surface Withdrawn EP1793188A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP05026438A EP1793188A1 (fr) 2005-12-05 2005-12-05 Condenseur à surface

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05026438A EP1793188A1 (fr) 2005-12-05 2005-12-05 Condenseur à surface

Publications (1)

Publication Number Publication Date
EP1793188A1 true EP1793188A1 (fr) 2007-06-06

Family

ID=36123972

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05026438A Withdrawn EP1793188A1 (fr) 2005-12-05 2005-12-05 Condenseur à surface

Country Status (1)

Country Link
EP (1) EP1793188A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015107314A1 (fr) * 2014-01-20 2015-07-23 Vallourec Heat Exchanger Tubes Tube amélioré pour échangeur thermique

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3217799A (en) * 1962-03-26 1965-11-16 Calumet & Hecla Steam condenser of the water tube type
GB1230196A (fr) * 1968-05-31 1971-04-28
GB1256278A (en) * 1968-04-17 1971-12-08 Saline Water Conversion Corp Improvements in condensers and condenser tubes therefor
US3779312A (en) * 1972-03-07 1973-12-18 Universal Oil Prod Co Internally ridged heat transfer tube
JPS5199707A (ja) * 1975-02-28 1976-09-02 Hitachi Ltd Netsukokanki
GB2043867A (en) * 1979-02-27 1980-10-08 Gen Atomic Co Heat Transfer Tube and Method of Making Same
FR2641066A1 (en) * 1988-12-22 1990-06-29 Orleans Universite Improvement to fluid condenser tubes with longitudinal fins and condensers using such tubes
RU2000531C1 (ru) * 1991-04-25 1993-09-07 Герман Николаевич Ерченко Вертикальна труба конденсатора

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3217799A (en) * 1962-03-26 1965-11-16 Calumet & Hecla Steam condenser of the water tube type
GB1256278A (en) * 1968-04-17 1971-12-08 Saline Water Conversion Corp Improvements in condensers and condenser tubes therefor
GB1230196A (fr) * 1968-05-31 1971-04-28
US3779312A (en) * 1972-03-07 1973-12-18 Universal Oil Prod Co Internally ridged heat transfer tube
JPS5199707A (ja) * 1975-02-28 1976-09-02 Hitachi Ltd Netsukokanki
GB2043867A (en) * 1979-02-27 1980-10-08 Gen Atomic Co Heat Transfer Tube and Method of Making Same
FR2641066A1 (en) * 1988-12-22 1990-06-29 Orleans Universite Improvement to fluid condenser tubes with longitudinal fins and condensers using such tubes
RU2000531C1 (ru) * 1991-04-25 1993-09-07 Герман Николаевич Ерченко Вертикальна труба конденсатора

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
DATABASE WPI Section Ch Week 199406, Derwent World Patents Index; Class J01, AN 1994-046851, XP002377204 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2015107314A1 (fr) * 2014-01-20 2015-07-23 Vallourec Heat Exchanger Tubes Tube amélioré pour échangeur thermique
FR3016689A1 (fr) * 2014-01-20 2015-07-24 Vallourec Heat Exchanger Tubes Tube ameliore pour echangeur thermique
CN106104190A (zh) * 2014-01-20 2016-11-09 尼奥迪斯有限公司 用于热交换器的改进的导管
JP2017503146A (ja) * 2014-01-20 2017-01-26 ネオティス エスアーエスＮｅｏｔｉｓｓ Ｓａｓ 改善された熱交換器用チューブ

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