EP0369298A1 - Luftgekühlter Dampfkondensator mit Vakuum und Schutz gegen Vereisung - Google Patents

Luftgekühlter Dampfkondensator mit Vakuum und Schutz gegen Vereisung Download PDF

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Publication number
EP0369298A1
EP0369298A1 EP89120617A EP89120617A EP0369298A1 EP 0369298 A1 EP0369298 A1 EP 0369298A1 EP 89120617 A EP89120617 A EP 89120617A EP 89120617 A EP89120617 A EP 89120617A EP 0369298 A1 EP0369298 A1 EP 0369298A1
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EP
European Patent Office
Prior art keywords
steam
tubes
input
tube
turbine
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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.)
Ceased
Application number
EP89120617A
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English (en)
French (fr)
Inventor
Michael William Larinoff
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Individual
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Individual
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Publication of EP0369298A1 publication Critical patent/EP0369298A1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • F28B9/005—Auxiliary systems, arrangements, or devices for protection against freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B9/00—Auxiliary systems, arrangements, or devices
    • F28B9/10—Auxiliary systems, arrangements, or devices for extracting, cooling, and removing non-condensable gases
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28B—STEAM OR VAPOUR CONDENSERS
    • F28B1/00—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser
    • F28B1/06—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium
    • F28B2001/065—Condensers in which the steam or vapour is separate from the cooling medium by walls, e.g. surface condenser using air or other gas as the cooling medium with secondary condenser, e.g. reflux condenser or dephlegmator

Definitions

  • This invention relates to improved freeze protected, air-cooled, vacuum steam condensers serving steam turbine power cycles or the like and, more particularly, to improved apparatus for condensing steam or other vapors in extremely cold climates and draining the condensate over a wide range of loads, pressures and ambient air temperatures and for also completely removing the steam-transported, undesirable, non-condensible gasses that migrate and collect at the end of the steam condensing system.
  • One technique for generating mechanical energy is the use of a turbine, boiler and an array of coupling conduits. Water is first converted to steam in the boiler. The steam is then conveyed to the turbine wherein the steam is expanded in its passage through rotating blades thereby generating shaft power. An array of conduits couple the turbine and the boiler and also define a working fluid return path from the turbine back to the boiler through steam condenser mechanisms in a continuing cycle of operation.
  • Steam condenser mechanisms include air-cooled vacuum steam condensers which may be considered as being comprised of four basic elements or systems: the steam condensing system, the air moving system, the condensate drain system and the non-condensible gas removal system.
  • an object of this invention to provide an improved steam power system comprising a turbine for converting steam energy into mechanical energy upon expansion of steam therein, a boiler for generating steam to be fed to the turbine, and a conduit arrangement coupling the boiler to the turbine input and then coupling the turbine exhaust to the boiler through steam condensing mechanisms, the condensing mechanisms including a plurality of U-shaped tubes through which the expanded steam flows and is condensed; front header means at the input ends of the tubes located in the cooler ambient air exposed regions of the tubes for receiving exhaust steam from the turbine; rear header means at the output ends of the tubes located in the warmer unexposed regions of the tubes for receiving condensate and non-condensible gasses; and means in the rear headers to remove non-condensible gasses from the rear headers, the tubes being designed and constructed to protect the exposed tubes from freezing for lack of steam by employing a tube arrangement that normally flows a steam quantity from the input headers not only for its exposed single row condensing duty but also for a second row as well
  • the invention may be incorporated into an improved steam powered system comprising a turbine for converting steam energy into mechanical energy upon expansion of steam therein, a boiler for generating steam to be fed to the turbine, and a conduit arrangement coupling the boiler to the turbine input and then coupling the turbine exhaust to the boiler through steam condensing mechanisms, the condensing mechanisms including a plurality of U-shaped tubes through which the expanded steam flows and is condensed; front header means at the input ends of the tubes located in the cooler ambient air exposed regions of the tubes for receiving exhaust steam from the turbine; rear header means at the output ends of the tubes located in the warmer unexposed regions of the tubes for receiving condensate and non-condensible gasses; and means in the rear headers to remove non-condensible gasses from the rear headers, the tubes being designed and constructed to protect the exposed tubes from freezing for lack of steam by employing a tube arrangement that normally flows a steam quantity from
  • the invention may also be incorporated into an apparatus for use in condensing steam including input header means, output header means and a plurality of sets of tubes each in a U-shaped configuration and together forming a bundle, each tube having an input length terminating at an input end and an output length terminating at an output end and with a bight therebetween, each tube coupling a front header means with a rear header means and with the lengths arranged in four (4) rows, the input lengths constituting the first and fourth rows and with the output lengths constituting the second and third rows.
  • the invention may be incorporated into an apparatus for use in condensing steam including input header means, output header means and a plurality of sets of tubes each in a U-shaped configuration, each tube having an input length terminating at an input end and an output length terminating at an output end and with a bight therebetween, each tube coupling a front header means with a rear header means and with the output ends of the tubes being positioned between the input lengths of each pair for the thermal protection thereof.
  • the front header means for each tube pair and the rear header means for each tube pair are spaced from each other a distance equal to about half the length of each tube.
  • the front and rear header means for each pair are located adjacent to the input and output ends of the tubes.
  • a power system 10 for converting thermal energy into mechanical energy.
  • the system includes a boiler 12 for generating steam and a turbine 14 which expands the high pressure steam thereby converting its energy into shaft power.
  • the waste steam exhausted from the turbine is condensed in an air-­cooled steam condenser 18 and the condensate is returned to the power cycle via conduits 16 and auxiliaries.
  • the steam condensing mechanism 18 consists of sub-systems which may be considered as including a steam condensing system 22, an air moving system 24, a condensate drain system 26 and a gas removal vacuum system 28.
  • the steam condensing mechanism employed in the preferred embodiment of the present invention consists of a main steam duct 33 feeding a steam supply duct 35 to which the steam condensing bundles 56 are attached at the front header.
  • the exhaust steam flows nearly horizontally inside the bundles through a plurality of parallel finned U-shaped tubes 32 where it is condensed and the condensate runs in parallel with the steam toward the rear headers.
  • the bundles are arranged in two (2) banks in an A-frame configuration.
  • the air-cooled steam condensing system employed in this invention may be considered as consisting of co­current air flow, two (2) pass steam flow, parallel condensate and steam flow inside the tubes, four (4) rows and a triangular pitch tube arrangement with the tubes installed perpendicular to the bundle frame.
  • the four (4) row bundle 56 consists of two (2) U-tubed elements 67 and 68 as shown in Figure 4 with two (2) front headers 36 and 38 and two (2) rear headers 37 and 39.
  • the two (2) faces of the bundles which are exposed to the ambient air have tube rows connected directly to the front headers respectively. Their rear headers and their corresponding tube rows are located inside the bundle.
  • the tubes 32 are provided with fins 52 to facilitate and promote more efficient heat transfer.
  • the heat transfer involves the flow of ambient air 50 over the finned tubes for cooling purposes to condense the steam into water.
  • the ambient air first contacts row 60 and then passes successively through rows 62, 64 and 66 where it is finally discharged as hot air back to the atmosphere.
  • the finned tubes are inclined from the horizontal sufficiently to provide gravity flow of the condensate to the ends of the tubes.
  • Figure 6 shows the A-frame bundle inclined "Y" degrees from the horizontal while the U-tube element is inclined “Z” degrees from the end of the bundles.
  • the angle "Y” can be decreased approaching the horizontal by increasing the "Z” angle another step in the triangular pitch configuration. This may be desirable for some installations.
  • This bundle design can be operated from a vertical position to some minimum tilt angle which is required for proper condensate drainage.
  • a cold weather steam condenser offers its first row of tubes which are exposed to the ambient air, particularly the ends of the tubes which are also the terminal ends of the steam-travel path in some designs. The condensate flows through these tube ends and if there is no steam present, there is danger of freeing. To insure that there is steam present at the tube ends of the first row, some manufacturers have designed their bundle steam flow path so that the first row of tubes 60 are used as a conduit for additional steam to be condensed either in the second row 62 or in a vent/dephlegmator section which follows the primary condenser.
  • the first row 60 should experience excessively high air-side heat transfer rates for whatever reasons, then it condenses its normal steam quantity plus that additional quantity which was slated as blow-through steam for the higher row 62 or vent/dephlegmator sections.
  • This blow-­through steam acts as a safety steam-reservoir for the first row of tubes by giving it the additional protective steam supply it needs, when it needs it.
  • the higher-row steam condensing surfaces 62 that have been robbed of steam are not adversely affected and the condensate that flows through them is in no danger of freezing since these tubes are located in the heated regions of the bundle.
  • the new steam condenser design of the instant invention offers added protection against freezing to the top rows of exposed tubes 66 that the other aforementioned condenser designs do not have.
  • This protection is built into the bundle fluid flow paths as shown in Figure 4.
  • This is a U-tube, two-pass steam condenser which has its steam supply connected direct to both the first and last rows, 60 and 66, of tubes which are the most vulnerable to freezing. These two rows have the first call on the steam that enters the bundle. If one of these two rows has a higher heat transfer rate for reasons of a higher air flow rate and/or a lower air temperature, steam will automatically be drawn to its surfaces at the expense of the less favored row.
  • top row 66 will divert steam from bottom row 60 and in doing so will starve rows 62 and 64. If rows 62 and 64 do not receive any steam, this presents no problem since these rows are in the warm internal zone of the bundle where moisture and condensate inside the tubes will not freeze.
  • bottom row 60 needs to protect itself it will automatically divert steam from top row 66 and in turn starve rows 62 and 64. Theoretically, it might be said that this four (4) row bundle heat-transfer surface automatically adjusts itself to become a one-plus (1+) row bundle when the external steam condensing conditions of rows 60 and 66 require this.
  • this bundle design has a low internal steam pressure drop. It is low because its tube length is less than twice the bundle width and it has no secondary condensers, vent condensers, dephlegmators, etc. This low pressure drop remains the same for all practical purposes irrespective of the bundle length and/or fan diameter. This low internal steam pressure drop allows the steam turbine to operate at a lower exhaust pressure which in turn improves the plant thermal efficiency.
  • the superior benefits and results of the present invention are attained by the relationship of the front and rear headers and their associated U-shaped steam condensing tubes with fins as shown Figure 4.
  • the tubes are arranged in pairs with each tube having its associated input and output headers located adjacent each other.
  • the associated front and rear headers with each tube pair are positioned spaced from each other by a distance substantially equal to half the length of the tubes if they were elongated and not bent.
  • Each tube has a first or input length coupled at its input end to its front header.
  • the input length extends to a bight in the tube and then returns parallel along a second or output length.
  • the output length terminates at its output end at a rear header.
  • the tubes of each pair are of similar construction but of opposite orientation in Figure 4.
  • the output end of each tube and its associated output header are in close proximity to its input end and its associated input heater.
  • Each output end and its associated header is located between the input lengths of the tubes of each pair and adjacent to its associated input headers.
  • the tube lengths for each tube pair are thus located in four (4) rows with the second and third lengths, with lesser steam, between the first and fourth lengths, with greater steam.
  • the rear headers and the output lengths of their tubes are thermally protected from the colder ambient air by the input headers and their associated input tube lengths which are exterior of the input tube lengths.
  • the front headers and input lengths are exposed to greater blasts of coldness but have greater steam quantities available to them for withstanding such coldness.
  • FIG 16. An alternate embodiment of the present invention is shown in Figure 16.
  • the U-shaped finned tubes are also arranged in pairs. Their input ends, however, are coupled with a common front header means.
  • the tubes have input ends and lengths and a bight and again double back to their output ends with output lengths parallel with the input lengths.
  • the output ends terminate in rear headers located proximate each other as well as proximate the input header.
  • the input ends of the tubes as well as the rear headers are all located proximate each other interior of the input ends, input lengths and their point of coupling with the front header so as the same thermal protection is afforded to the output lengths and output headers as is afforded in the primary embodiment of Figure 4.
  • the air moving system 24 employed in the disclosed preferred embodiments of this invention is the conventional industry type shown in the patent literature. It preferably employs either mechanical draft fans 86, natural draft or some combination of both.
  • the fan arrangements can be either of the induced or forced draft type. In all cases the forced air flow across the outside of the finned tubes is the cooling medium that condenses the steam inside the tubes.
  • the condensate drain system starts at the bundle rear headers 37 and 39, Figure 15.
  • a detailed view of the rear header 39 is shown in Figure 10.
  • the condensate 20 flows from the rear header into a water leg 72 which is connected to a condensate manifold 82, Figures 1 and 15. From there it flows through an hydraulic balance device 90, Figure 14, and into the condensate storage tank 84 by gravity.
  • Condensate pumps 88 take suction from the storage tank and return the condensate back to the power cycle to repeat the process.
  • the bundle rear headers 37 and 39 operate at different steam pressures and therefore cannot be simply connected together. They are joined together at the condensate manifold 82 by means of water legs 70 and 72.
  • the steam pressure in rear header 37 is greater than the steam pressure in rear header 39 and as a result its water leg height H-1 is less than water leg height H-2 for rear header 39. Note Figure 15.
  • the hydraulic balance device 90 is the subject of the same Patent Application Serial Number 07/206,095 referenced in the preceding paragraph.
  • This device has several functions. The first is to provide a datum steam pressure from rear header 37 in chamber 98 against which the bundle rear header steam pressures and their corresponding water legs are hydraulically balanced. Its second function is to establish and maintain a pre­determined static water level datum line 92 which insures that each water leg is operational and that the water level does not drop below this minimum otherwise its water sealing properties would be destroyed. In normal operation the water level would rise above datum 92, Figure 14 and might approach a level such as 93, depending upon the flow quantities and friction pressure drop in the condensate piping. Vent tube 102 serves to purge chamber 98 of non-condensible gasses by the eduction process.
  • Each rear header has a suction sparger pipe 116 that runs the full length of the rear header as shown in Figure 10.
  • the suction sparger has a series of orifices 114 drilled along its entire length. The orifices are located so as to face a quiescent zone Figure 12 in­between the finned tube openings, Figure 10 with one orifice serving either one or a pair of tubes.
  • the non-condensible gasses and vapors are "sucked out" from the rear header through these orifices 114 by the action of he steam jet air ejection equipment. Any condensate that enters the suction sparger drains by gravity through orifice 115 located at the bottom of the sparger pipe.
  • the gasses and vapors travel out of the suction spargers into a piping manifold 120 and 122, one for all the lower U-tube rear headers 39 and the other for all the upper U-tube rear headers 37. These rear headers cannot be tied together because they have different gas/vapor pressures due to their relative location in the bundle.
  • the gas/vapors flow from the manifolds into the vacuum inducing first-stage ejectors 144. Note Figure 15.
  • the discharged mixture from the two (2) ejectors are now at the same pressure so that they can be mixed and piped direct to the inter-condenser 150.
  • This air ejection package 130 is a conventional two-stage steam ejector unit with inter-condensers and after-­condensers. Motor driven vacuum pumps with or without air ejectors could be readily substituted for the steam operated device shown.
  • the drilled orifices of the suction sparger are of different diameters (i) along the length of the sparger, (ii) rear header sparger 37 compared to rear header sparger 39 (iii) amongst bundles themselves. They are different diameters for different reasons. In the first case the orifice openings near the open/exhaust end of the sparger will be slightly smaller than the orifices near the closed end because of internal frictional pressure drops through the length of the sparger pipe. In the second case the gas/vapor mixture pressure in rear header 37 is higher than the pressure in rear header 39. This requires different orifice diameters to achieve design flow rates.
  • the bundles located close to the first-stage ejectors would normally tend to flow a larger quantity of gas/vapor than the bundles located further away at the end of the tower.
  • the object in all of these orifice drillings is to extract the same mass quantity of gas/vapor from each and every bundle in the tower, and similarly, to extract equal mass quantities of gas/vapor from each increment of rear header length.
  • This gas/vapor extraction system is a fundamental improvement over the known present day systems.
  • the present day gas/vapor extraction system does not have a suction sparger 116. It has an extraction pipe welded to the top of the rear header closure plate which would look similar to Figure 13.
  • This single pipe opening at the top of the rear header is expected to evacuate a rear header that may be about twenty (20) to over thirty (30) feet long in some designs. In reality what it is evacuating is mostly steam vapor blow-through that comes from the uppermost tubes of the bundle, close to the suction opening.
  • the single suction opening at the top of the rear header cannot distinguish the non-condensible gasses from the steam vapor as it will move whatever fluid is closest to it.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP89120617A 1988-11-14 1989-11-07 Luftgekühlter Dampfkondensator mit Vakuum und Schutz gegen Vereisung Ceased EP0369298A1 (de)

Applications Claiming Priority (2)

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US27065688A 1988-11-14 1988-11-14
US270656 1994-07-05

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EP0369298A1 true EP0369298A1 (de) 1990-05-23

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EP89120617A Ceased EP0369298A1 (de) 1988-11-14 1989-11-07 Luftgekühlter Dampfkondensator mit Vakuum und Schutz gegen Vereisung

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EP (1) EP0369298A1 (de)
JP (1) JPH02252906A (de)
ZA (1) ZA898684B (de)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0545366A1 (de) * 1991-12-05 1993-06-09 Michael William Larinoff Luftgekühlter Vakuum-Dampfkondensator mit Kleinbündeln mit Ausgleich des Durchflusses
DE102013106329A1 (de) * 2013-06-18 2014-12-18 Gea Energietechnik Gmbh Verfahren und Anordnung zum Evakuieren eines Rohrleitungssystems
CN104613790A (zh) * 2014-12-19 2015-05-13 北京龙源冷却技术有限公司 间接空冷系统扇段防冻方法
CN108507369A (zh) * 2018-05-31 2018-09-07 西安热工研究院有限公司 一种用于直接空冷岛的导流防冻集成装置
CN109328290A (zh) * 2016-06-21 2019-02-12 艾威普科公司 全次级的空气冷却式工业蒸汽冷凝装置
CN111397389A (zh) * 2020-03-20 2020-07-10 太原理工大学 一种防止管束冻结的电厂直接空冷系统
CN113670087A (zh) * 2021-09-06 2021-11-19 神华国能宁夏鸳鸯湖发电有限公司 一种间接空冷塔分压防冻装置及方法

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105114139B (zh) * 2015-09-21 2017-03-08 刘钊 一种带有立式三角形式干式空冷凝汽器的直接空冷系统

Citations (7)

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Publication number Priority date Publication date Assignee Title
US2816738A (en) * 1956-02-17 1957-12-17 John J Nesbitt Inc Heat exchanger
US3289742A (en) * 1962-09-19 1966-12-06 Niemann Johann Christoph Air cooled surface condenser and method of operating the same
US3705621A (en) * 1971-06-25 1972-12-12 Lummus Co Air-cooled heat exchanger
US3887002A (en) * 1974-01-28 1975-06-03 Lummus Co Air-cooled heat exchanger with after-condenser
US4202405A (en) * 1972-09-25 1980-05-13 Hudson Products Corporation Air cooled condenser
GB2093176A (en) * 1981-02-18 1982-08-25 Nuovo Pignone Spa Air cooled condenser
US4417619A (en) * 1978-06-05 1983-11-29 Sasakura Engineering Co., Ltd. Air-cooled heat exchanger

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2816738A (en) * 1956-02-17 1957-12-17 John J Nesbitt Inc Heat exchanger
US3289742A (en) * 1962-09-19 1966-12-06 Niemann Johann Christoph Air cooled surface condenser and method of operating the same
US3705621A (en) * 1971-06-25 1972-12-12 Lummus Co Air-cooled heat exchanger
US4202405A (en) * 1972-09-25 1980-05-13 Hudson Products Corporation Air cooled condenser
US3887002A (en) * 1974-01-28 1975-06-03 Lummus Co Air-cooled heat exchanger with after-condenser
US4417619A (en) * 1978-06-05 1983-11-29 Sasakura Engineering Co., Ltd. Air-cooled heat exchanger
GB2093176A (en) * 1981-02-18 1982-08-25 Nuovo Pignone Spa Air cooled condenser

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0545366A1 (de) * 1991-12-05 1993-06-09 Michael William Larinoff Luftgekühlter Vakuum-Dampfkondensator mit Kleinbündeln mit Ausgleich des Durchflusses
DE102013106329A1 (de) * 2013-06-18 2014-12-18 Gea Energietechnik Gmbh Verfahren und Anordnung zum Evakuieren eines Rohrleitungssystems
DE102013106329B4 (de) * 2013-06-18 2015-04-09 Gea Energietechnik Gmbh Verfahren und Anordnung zum Evakuieren eines Rohrleitungssystems
CN104613790A (zh) * 2014-12-19 2015-05-13 北京龙源冷却技术有限公司 间接空冷系统扇段防冻方法
CN109328290A (zh) * 2016-06-21 2019-02-12 艾威普科公司 全次级的空气冷却式工业蒸汽冷凝装置
CN108507369A (zh) * 2018-05-31 2018-09-07 西安热工研究院有限公司 一种用于直接空冷岛的导流防冻集成装置
CN111397389A (zh) * 2020-03-20 2020-07-10 太原理工大学 一种防止管束冻结的电厂直接空冷系统
CN111397389B (zh) * 2020-03-20 2021-07-27 太原理工大学 一种防止管束冻结的电厂直接空冷系统
CN113670087A (zh) * 2021-09-06 2021-11-19 神华国能宁夏鸳鸯湖发电有限公司 一种间接空冷塔分压防冻装置及方法
CN113670087B (zh) * 2021-09-06 2024-04-26 神华国能宁夏鸳鸯湖发电有限公司 一种间接空冷塔分压防冻装置及方法

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Publication number Publication date
ZA898684B (en) 1991-03-27
JPH02252906A (ja) 1990-10-11

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