WO2014122493A1 - Triangle de refroidissement pour un système de refroidissement à sec - Google Patents

Triangle de refroidissement pour un système de refroidissement à sec Download PDF

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Publication number
WO2014122493A1
WO2014122493A1 PCT/HU2014/000016 HU2014000016W WO2014122493A1 WO 2014122493 A1 WO2014122493 A1 WO 2014122493A1 HU 2014000016 W HU2014000016 W HU 2014000016W WO 2014122493 A1 WO2014122493 A1 WO 2014122493A1
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WO
WIPO (PCT)
Prior art keywords
cooling
tubes
columns
delta
tube bundle
Prior art date
Application number
PCT/HU2014/000016
Other languages
English (en)
Inventor
Gábor Csaba
Csaba BANNERTH
Original Assignee
Gea Egi Energiagazdálkodási Zrt.
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 Egi Energiagazdálkodási Zrt. filed Critical Gea Egi Energiagazdálkodási Zrt.
Priority to RU2015135134A priority Critical patent/RU2645817C2/ru
Priority to CN201480008196.7A priority patent/CN105008846B/zh
Priority to EP14719525.9A priority patent/EP2954277A1/fr
Priority to US14/765,070 priority patent/US20150377559A1/en
Publication of WO2014122493A1 publication Critical patent/WO2014122493A1/fr
Priority to ZA2015/05558A priority patent/ZA201505558B/en

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/0408—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids
    • F28D1/0426—Multi-circuit heat exchangers, e.g. integrating different heat exchange sections in the same unit or heat exchangers for more than two fluids with units having particular arrangement relative to the large body of fluid, e.g. with interleaved units or with adjacent heat exchange units in common air flow or with units extending at an angle to each other or with units arranged around a central element
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • 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

Definitions

  • the invention relates to a cooling delta applicable for a dry cooling system.
  • the deltas of which each consists of two heat exchanger bundles 1 arranged at an angle relative to each other, are assembled by means of a common steel structure 8, each delta thereby forming an individual assembly unit.
  • This critical water flow value is determined by two factors. One of these is the water-side resistance of the cooling tubes 2, the other factor (closely related to the first one) is the inlet velocity at which erosion may begin to occur at the cooling tube inlets. To better understand this, consider that the larger the extracted thermal power is, the larger the water flow will be. In proportion to the increasing thermal power, the air flow should also increase, which goes hand in hand with the increasing combined front surface area of the heat exchanger bundles 1 that have to be built in. This increased front surface area may be provided by increasing the circumference of the cooling tower, as well as the height of the cooling column 7.
  • both the base diameter of the cooling tower and the height of the cooling columns 7 should be increased by a factor of V2.
  • the critical inlet velocity is reached in case of a conventional power plant of 500-700 MW, and a nuclear power plant of 300-500 MW.
  • the tube velocity may of course be reduced by applying multiple tube rows. This solution is, however, limited by the increasing airside resistance of the heat exchanger, which in case of natural draft necessitates an increase of tower height, and in case of using fans the energy expenses of the self-consumption increase.
  • the tube velocity may also be reduced by applying larger diameter tubes, as illustrated in the top drawing of Fig. 2.
  • This solution also has its limits, namely that relative to the unit front surface area of the heat exchanger bundle 1 an increasing portion of the cross-section available for the free flow of air is taken up by the larger-diameter cooling tubes 2.
  • tower height is increased due to increasing air resistance, while in case of using fans the energy consumption of the tower is increased.
  • the horizontally measurable length of the heat exchangers has to increase, which increases the circumference of the tower. It could also be possible to increase the number of the applied cooling towers. However, this option is much more costly compared to single-tower solutions.
  • the primary object of the invention is to provide a cooling delta which are free of the disadvantages of the prior art solutions to the greatest possible extent.
  • the objects of the invention can be achieved by the cooling delta according to claim 1.
  • Preferred embodiments of the invention are defined in the dependent claims.
  • the cooling delta according to the invention is adapted for cooling liquid, gaseous or steam media to be cooled (in the following: media).
  • the cooling delta according to the invention comprises cooling panels arranged at an angle relative to one another, in which cooling panels cooling tubes are arranged.
  • the cooling tubes extend horizontally or substantially horizontally
  • the cooling delta further comprises a first media flow header - arranged preferably vertically or substantially vertically - being connected to the cooling tubes at a junction of the cooling panels, and providing a flow communication space for the cooling tubes, and second media flow headers - arranged preferably vertically or substantially vertically - connected to opposite ends of the cooling panels with respect to the first media flow header, and providing a flow communication space for the cooling tubes.
  • the media flow headers are preferably implemented as chambers.
  • the cooling tubes extend horizontally or substantially horizontally, which is to be meant that the cooling tubes may have a maximum inclination of a few degrees. In some embodiments, a slight inclination is explicitly required; however, in conventional cooling deltas the cooling tubes are arranged vertically, from which the horizontal or substantially horizontal arrangement of the cooling tubes is fundamentally different.
  • the first media flow header and/or the second media flow headers are formed as columns.
  • loading forces arising from the weight of the cooling columns and from wind load act on the outside and inside support columns partly via the steel structure, and partly via the flat surfaces of the support columns, which surfaces comprise openings or bores and are adapted for holding together the cooling tubes.
  • Fig. 1 is a drawing of a prior art cooling delta that has heat exchanger bundles 1 and cooling columns 7, inlet and outlet chambers 4 and return chambers 5, chamber stubs 6 and a steel structure 8,
  • Fig. 2 shows a magnified view of a component of a prior art cooling delta that has cooling tubes of two different diameters, illustrating the cooling tubes 2 and cooling fins 3,
  • Fig. 3 shows a prior art multi-storey cooling delta arrangement comprising distribution conduits 9,
  • Fig. 4 illustrates the delta arrangement according to the invention, showing the inside support columns 10, the outside support columns 11 , and particularly in- and outlet, inlet, outlet and return chambers for media flowing, all integrated in the support column,
  • Fig. 5 shows magnified detail views of the media flow chambers integrated in the inside support columns 10 and outside support columns 11 arranged according to Fig. 4,
  • Fig. 6 shows a top plan view of the flow pattern that occurs in a cross section of the delta in case of side wind
  • Fig. 7 shows an embodiment of the delta arrangement according to the invention, the deltas having cooling panels 19 arranged at two sides of the delta extending to the full height and width thereof, cooling columns 7 arranged horizontally in the cooling panels 19, inside support columns 10, outside support columns 11 , a steel structure 8, the drawing also showing arrows indicating the flow direction of the media to be cooled,
  • Fig. 8 illustrates the interconnections applied in the example of Fig. 7, showing cut out details of the horizontal cooling column 7, the fixed tube bundle sheets 12 and loose tube bundle sheets 13, 22, a transition piece 15, rubber rings 17, cut out portions of the inside support columns 10 and outside support columns 11 adapted for flowing the media, and, towards the bottom, right- and left-side details of the cooling column illustrating the different assembly and disassembly positions
  • Fig. 9 shows exemplary connection options of the cooling panels 19
  • Fig. 10 shows implementations of the tube bundle sheet connections applying, respectively, rubber plates 26, and a combination of rubber plates 26 and O- rings 17. MODES FOR CARRYING OUT THE INVENTION
  • the solution according to the invention provides an alternative of the prior art solutions (see Figs. 4, 5, 6, 7, 9) by arranging the cooling columns 1 and thereby the cooling tubes 2 horizontally, or substantially horizontally, while keeping the advantageous vertical arrangement of the cooling delta.
  • the ends of tubes are passed through bores arranged on the vertical support columns of the - otherwise necessarily applied - delta structure, and are introduced into inlet and outlet chambers 4, or, without applying these, directly into the inside support column 10 or outside support column 11.
  • multiple horizontal cooling columns 7, stacked above one another constitute a cooling panel 19.
  • the chambers 4, 5 may be arranged at the other side (not shown) of the support columns, while in the latter case they are formed integrated in the support columns 10, 11.
  • the bores receiving the cooling tubes are disposed on the support columns 10, 11 themselves (see 14, Fig. 8), and the support columns are implemented as enclosed structures. This arrangement provides that the water flows through an enclosed space into and out of the cooling tubes 2 of the heat exchanger bundles 1.
  • the tubes While in conventional cooling deltas the length of the cooling tubes reaches 25-30 m, in the cooling delta according to the invention the tubes may be much shorter.
  • the reduced tube length involves reducing the flow speed of water in the heat exchanger tubes, with the water side resistance also decreasing according to the third power.
  • the horizontal width of the heat exchanger bundles built into conventional cooling deltas is 2.5-2.7 m.
  • the bundles of the cooling delta according to the invention may exceed that by a factor of 3 to 5.
  • the combination of these features allow that the 600-700 MW power limit for single-tower dry cooling systems applied for conventional power stations may be raised to 1200-1600 MW, also allowing the application of the single-tower system for 800-1200 MW PWR or BWR nuclear power station blocks.
  • the inventive solution has further important advantages, namely that it reduces the sensitivity to wind and the danger of freezing damage that conventional cooling towers having vertically arranged tubes are subjected to. This may be understood contemplating Fig. 6.
  • the flow pattern in wind is shown for a cooling delta arranged at the side of the tower.
  • the tubes situated at the outside portion 20 of the cooling column shown in the right of the drawing may be overcooled, or, in winter, may be damaged by freezing.
  • This is related to the vertical arrangement of the tubes, as the high air flow density affects the entire length of the cooling tubes in question.
  • the cooling tubes 2 situated in the inside portion 21 of the left-side cooling column Conversely, due to the depression, the cooling tubes 2 of the outside portion of the upwind column provide little or no cooling.
  • the heat exchanger tubes are prone to freezing damage, and, in addition to that, the cooling power of the cooling tower is also reduced, which poses problems of operation especially in case of winds occurring in the hottest summer period.
  • the deltas illustrated in Fig. 7 have two cooling panels 19 arranged at an angle relative to each other and facing to each other. Parallelly arranged, horizontally extending cooling columns 7 are arranged in the cooling panels 19.
  • the cooling columns 7 consist of one or more heat exchanger bundle 1 or bundles connected to each other (the attachments are not shown in themselves).
  • the heat exchanger bundle 1 is the smallest heat exchanger assembly unit of the cooling column 7, i.e. the smallest unit to which the column may be disassembled without cutting.
  • the cooling columns 7, consisting of one or more interconnected heat exchanger bundle 1 or bundles 1 can be integrally removed from the delta.
  • the cooling column has the same width as the cooling components, and its width cannot be further reduced without cutting.
  • the cooling columns 7 are manufactured by joining at least one end of each cooling tube 2 to a tube bundle sheet (or tubesheet) made from continuous plates applying rolling, welding, or any other technology that produces permanent joints.
  • the major constituent parts of the steel structure 8 adapted for supporting the cooling delta are the three - vertical or substantially vertical - inside 10 and outside support columns 1 1 situated in the three corners of the delta.
  • the surfaces of the support columns facing the cooling columns are machined flat to form flat walls 14, and are configured to comprise bores arranged in a pattern corresponding to the arrangement of the cooling tubes 2 in the heat exchanger bundle 1 .
  • the flat wall 14 constitutes either a flat surface or the tube bundle sheet itself through which the media flows to and from the cooling tubes 2.
  • a plurality of cooling columns 7 are connected to each support column pair made up of an inside support column 10 and an outside support column 1 1.
  • the bored flat walls 14 of the corresponding inside support columns 10 and outside support columns 1 1 are arranged parallel with each other.
  • the steel structure 8 of the delta, and thereby the inside and outside support columns 10, 1 1 are fixedly secured. This constraint has to be borne in mind when producing the cooling columns 7 so as to allow them to be removed from between the inside and outside support columns 10, 1 1.
  • a possible embodiment of the invention is presented as follows.
  • a solution extensively applied in conjunction with dry cooling towers is sealing the ends of the cooling tubes 2 by means of rubber rings 17. Such a solution is shown in Fig. 8, in the groove extending between the loose tube bundle sheet 13, the flat wall 14, and the cooling tube 2.
  • the primary advantage of this solution is that the costly welding-in process of the cooling tubes 2 may be omitted.
  • Another advantage is that it is capable of simultaneously sealing the gaps between the cooling tube 2 and the loose tube bundle sheet 13 and between the loose tube bundle sheet 3 and the flat wall 14 (in this case, the support column wall).
  • This sealing solution also allows - and it has not been applied so far - that the loose tube bundle sheet 13 situated at the end portion of the heat exchanger may be inserted in place loosely, without rolling.
  • This allows that a fully installed cooling column may be pulled out from the flat wall 14, i.e. in the present case from the bores of the flat wall 14 formed integrally with the support column 18, in a direction parallel with the tube axis. All that has to be done is to loosen the tube bundle sheet screws 16 joining the tube bundle sheets.
  • cooling tubes 2 of the cooling blocks of the heat exchanger should be arrested in the longitudinal direction in at least one plane perpendicular to the tubes. To achieve that, it is imperative that the cooling tubes 2 are rolled or welded into a fixed tube bundle sheet 12 on at least one side. One end of the cooling column 7 is therefore configured accordingly.
  • the axial displaceability of the cooling tubes 2 is provided for by extending the end of the cooling tubes 2 over the tube bundle sheet to the required extent.
  • the cooling column 7 Since the cooling column 7 must be fixed in the axial direction, for which the rubber rings are not sufficient, a fixed connection must be provided between the fixed tube bundle sheet 12, disposed at this end of the cooling column 7 and adapted to fixedly engage the tubes, and the flat wall 14 formed on the support column. In addition to that, it should also be provided that, in case this fixed connection is loosened, the free tube ends of the cooling column 7 may be slid into the inside support column 10 through the bores thereof adapted for receiving the cooling tubes 2. This is achieved by applying the following solution:
  • Rubber rings 17 are placed on the distal side of the loose tube bundle sheet, on the ends of the cooling tubes 2.
  • the rubber rings 17 situated between the loose tube bundle sheet 13 and the flat wall 14 functioning as the sealing surface of the inside support column 10 are constricted by inserting such transition pieces 15 between the fixed tube bundle sheet 12 and the loose tube bundle sheet 13 that are resilient, but fixed enough to transfer a pressure force to the loose tube bundle sheet 13 that is sufficient to provide the required sealing effect by deforming the rubber rings 17.
  • the cooling column 7 may be longitudinally displaced towards the inside of the inside support column 10 by an extent corresponding to the thickness of the transition piece 5. To achieve that, all that has to be done is to loosen the screws 23 of the loose tube bundle sheet 22 situated at the opposite side.
  • the thickness of the transition piece 5 is chosen such that on the other side the ends of the cooling tubes 2 may come out from bores of the outside support column 1 1.
  • the cooling column 7 may be removed by first lifting it at the - now freed up - side facing the outside support column 1 1 , and then pulling and lifting it out at the side facing the inside support column 10.
  • the spatial steel structure of the delta (not shown) is configured such that the side through which the damaged cooling columns 7 are to be removed is free, or arranged to be able to be freed up.
  • this sealing and tube bundle sheet attachment method does not require high manufacturing accuracy. It is not important that the flat walls 14 of the inside and outside support columns 10, 1 1 , being adapted for sealing, fall perfectly in the same plane. It is also not a problem if the sealing flat walls 14 of the respective inside and outside support columns 10, 11 facing each other are not perfectly parallel, and there can even be an angle allowance in their perpendicular angle relative to the cooling tubes 2. There can also be difference in the distances between the sealing flat walls 14 of the inside and outside support columns 10, 11. What is important is the positional accuracy of the bores disposed on the cooling columns, and the bores of the tube bundle sheets 12, 13, 14, but this requirement is not different from requirements set for conventional heat exchangers.
  • the connections between the cooling tubes 2 and the inside and outside support columns 10, 1 may be implemented as welded connections. In that case, the components designated by reference numerals 12, 13, 15, 16, 17, 22, 23 in Fig. 8 may be omitted. Damaged cooling tubes 2 may only be repaired in this case by destructively dismantling those surfaces of the corresponding inside and outside support columns 10, 11 that are situated facing the axes of the cooling tubes 2. At the end the repair operation, the dismantled support column must be reconstructed. This may be carried out by closing the previously cut out opening by welding.
  • FIG. 10 Another possible embodiment of the invention is illustrated in the top drawing of Fig. 10.
  • the fixed tube bundle sheets 12 of the cooling column 7 are connected at both ends of the cooling column 7 to the machined flat walls 14 of the inside and outside support columns 10, 11 by means of a respective sealing rubber plate 26.
  • the above described solution may also be realised (see the drawing at the bottom of Fig. 10) by for instance applying the latter rubber plate solution at the left-side connection, and the arrangement including rubber rings 17 shown in the right in Fig. 8 at the right-side connection.
  • the cooling column may be dismantled from the structure also in this case.
  • the circuit connection options of the heat exchangers implemented according to the invention are not different from those of conventional heat exchangers; full cross-flow being the simplest to implement.
  • the medium to be cooled flows in the same direction in all of the tubes of a given cooling column.
  • the cooling water inlet is at the outside support column 11 of the deltas, while the cooled down water is let out at the inside support column 10.
  • a reversed solution may also be possible, but, as it was shown in the above discussion on the danger of freezing damage, the former solution is more advantageous.
  • FIG. 9 The top left drawing of the figure illustrates the connection scheme of the embodiment described in relation to Fig. 7.
  • An alternative arrangement is also possible (top right drawing, Fig. 9) wherein for instance only the flow direction of the cooling water is changed at the inside support column 10, and the inlet and outlet are disposed on the two outside columns. In this case, each two adjoining cooling columns are connected serially on the water side.
  • a further possible solution bottom left drawing that one of the support columns is divided in two by a divider member 24 along a plane perpendicular to the longitudinal axis of the column, while the opposite column is left undivided.
  • two flow paths may be configured along the column's axis by installing inlet and outlet stubs on only the divided columns but not on the opposite ones, which latter columns therefore become adapted for only reversing the flow direction of the media.
  • more than two flow paths may also be formed.
  • a cross-counter-flow connection of the cooling columns may also be realised, as it is shown in the bottom right drawing in Fig. 9.
  • the outside support columns 11 may function as the common return chamber of the cross-counter-flow cooling panel 9 having separate inlets through the two inside support columns.
  • a similar solution may be provided by implementing the double water conduction in the outside support column 11. This may also be realised by arranging the water inlets and outlets exclusively at the bottom of the structure.
  • a solution for filling and draining the cooling deltas should also be found which provides that air can flow out from the cooling tubes during filling and water can flow out therefrom during draining. This may be achieved by raising to a small extent the axis of the cooling tubes 2 (seen from the direction of the inlet support column). The same effect may be obtained for instance by disposing the bores of the inside support column 10 a few centimeters higher, which is allowed by the resilient sealing method described above. According to this solution, the draining ports of the cooling delta are disposed at the bottommost portion of the inlet support columns.
  • cooling tubes 2 descend towards the direction of outflowing air (taking into account the filling direction).
  • the draining means is disposed at the bottommost portion of the outlet support column.
  • the hydraulic resistance of the cooling tube 2 must exceed the hydrostatic pressure difference caused by the height difference resulting from the tube's inclination.
  • the media enters the outside support column 1 1 at the bottom, and is let out at the top of the inside support column 10.
  • the deltas are filled also in this direction, such that air is let out at the top portion of the inside support column 10. Draining may be carried out in the opposite direction.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un triangle de refroidissement pour refroidir des liquides, des gaz ou des vapeurs, ledit triangle de refroidissement comprenant des panneaux de refroidissement agencés à un certain angle les uns par rapport aux autres, dans lequel sont agencés des tubes de refroidissement des panneaux de refroidissement, les tubes de refroidissement s'étendent horizontalement ou sensiblement horizontalement, et le triangle de refroidissement comprenant en outre un premier collecteur d'alimentation de milieu relié aux tubes de refroidissement à une jonction des panneaux de refroidissement, et établissant un espace de communication fluidique pour les tubes de refroidissement, et des seconds collecteurs d'alimentation de milieu reliés à des extrémités opposées des panneaux de refroidissement par rapport au premier collecteur d'alimentation de milieu, et établissant un espace de communication fluidique pour les tubes de refroidissement.
PCT/HU2014/000016 2013-02-11 2014-02-11 Triangle de refroidissement pour un système de refroidissement à sec WO2014122493A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
RU2015135134A RU2645817C2 (ru) 2013-02-11 2014-02-11 Охладительная дельта для системы сухого охлаждения
CN201480008196.7A CN105008846B (zh) 2013-02-11 2014-02-11 用于干式冷却系统的冷却三角
EP14719525.9A EP2954277A1 (fr) 2013-02-11 2014-02-11 Triangle de refroidissement pour un système de refroidissement à sec
US14/765,070 US20150377559A1 (en) 2013-02-11 2014-02-11 Cooling Delta For A Dry Cooling System
ZA2015/05558A ZA201505558B (en) 2013-02-11 2015-08-03 Cooling delta for a dry cooling system

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
HU1300085A HUP1300085A2 (en) 2013-02-11 2013-02-11 Heat exchanger unit for dry cooling towers
HUP1300085 2013-02-11

Publications (1)

Publication Number Publication Date
WO2014122493A1 true WO2014122493A1 (fr) 2014-08-14

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ID=89991033

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/HU2014/000016 WO2014122493A1 (fr) 2013-02-11 2014-02-11 Triangle de refroidissement pour un système de refroidissement à sec

Country Status (7)

Country Link
US (1) US20150377559A1 (fr)
EP (1) EP2954277A1 (fr)
CN (1) CN105008846B (fr)
HU (1) HUP1300085A2 (fr)
RU (1) RU2645817C2 (fr)
WO (1) WO2014122493A1 (fr)
ZA (1) ZA201505558B (fr)

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WO2016174481A1 (fr) * 2015-04-30 2016-11-03 Enexio Hungary Zrt. Tour de refroidissement présentant une structure de tour de forme circulaire ou polygonale

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WO2017031494A1 (fr) 2015-08-20 2017-02-23 Holtec International Système de refroidissement à sec destiné à des centrales électriques
US10161683B2 (en) 2015-08-20 2018-12-25 Holtec International Dry cooling system for powerplants
CN107560484B (zh) * 2016-06-30 2020-05-19 浙江盾安热工科技有限公司 连接件和微通道换热器
EP3287732B1 (fr) * 2016-08-24 2019-10-02 SPG Dry Cooling Belgium Condenseur refroidi par air à tirage induit
CN107702557A (zh) * 2017-11-07 2018-02-16 国电科学技术研究院 冷却柱及其防冻结构、冷却三角
DE102019110236A1 (de) * 2019-04-18 2020-10-22 Güntner Gmbh & Co. Kg Wärmeübertrageranordnung mit wenigstens einem Mehrpass-Wärmeübertrager und Verfahren zum Betrieb einer Wärmeübertrageranordnung

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CN105008846A (zh) 2015-10-28
RU2015135134A (ru) 2017-03-16
ZA201505558B (en) 2016-06-29
HUP1300085A2 (en) 2014-08-28
RU2645817C2 (ru) 2018-02-28
US20150377559A1 (en) 2015-12-31
CN105008846B (zh) 2017-11-14

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