EP1154216A1 - Dispositif pour chauffage de liquides à la vapeur - Google Patents

Dispositif pour chauffage de liquides à la vapeur Download PDF

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Publication number
EP1154216A1
EP1154216A1 EP00109947A EP00109947A EP1154216A1 EP 1154216 A1 EP1154216 A1 EP 1154216A1 EP 00109947 A EP00109947 A EP 00109947A EP 00109947 A EP00109947 A EP 00109947A EP 1154216 A1 EP1154216 A1 EP 1154216A1
Authority
EP
European Patent Office
Prior art keywords
liquid
heat exchanger
heater according
heat
exchanger package
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.)
Granted
Application number
EP00109947A
Other languages
German (de)
English (en)
Other versions
EP1154216B1 (fr
Inventor
Jiri Dipl.-Ing. Svoboda
Dirk Dipl.-Ing Kux
Heinz Borg
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 PHE GmbH
Original Assignee
Balcke Duerr Energietechnik GmbH
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 Balcke Duerr Energietechnik GmbH filed Critical Balcke Duerr Energietechnik GmbH
Priority to EP20000109947 priority Critical patent/EP1154216B1/fr
Priority to DE50001791T priority patent/DE50001791D1/de
Publication of EP1154216A1 publication Critical patent/EP1154216A1/fr
Application granted granted Critical
Publication of EP1154216B1 publication Critical patent/EP1154216B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
    • F28D9/0037—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the conduits for the other heat-exchange medium also being formed by paired plates touching each other
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/0006—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the plate-like or laminated conduits being enclosed within a pressure vessel

Definitions

  • the invention relates to a steam-heated liquid heater with one cuboid-shaped, composed of several profiled plates
  • Heat exchanger package with a first group of channels for the saturated or superheated steam and a substantially cross-flow second Group of channels for the heat-absorbing liquid, both the Channels of the first as well as the channels of the second group each on two opposite sides of the heat exchanger package open, and on arranged on the other two sides of the heat exchanger package pressure plates are that brace the profile plates arranged between them against each other.
  • Such devices are mainly used in power plant operation Liquid preheater used.
  • Liquid preheater used in a single, profiled plate composite and in its basic design, for example in EP 0 658 735 B1 described heat exchanger package is the superheated or saturated steam cooled and condensed, the released heat over the profiled Plates are released to the cross-flow liquid, causing this heats up.
  • the thin-walled profiled plates joined by welding are characterized by good heat exchange performance, but stand out This design also has problems with regard to strength, because above all when starting and shutting down the heat exchanger as a result mechanical structure multi-axis stress states can arise both on the prevailing pressure differences, as well as on those from the Strain stresses arising due to temperature differences.
  • the expansion stresses arise between the core of the heat exchanger and the housing parts, especially those with regard to the to be recorded Print relatively thick-walled side panels.
  • the thermal expansions work especially in the transition zones to the welds due to high local Tensions.
  • Welds are not only between the individual Sheets of the heat exchanger package, but also in the area of the edges where So-called corner welds are to be provided to the necessary mechanical To create strength and connectivity for the housing. in addition come material vibrations caused by pressure fluctuations in the media are excited and also lead to high local voltage peaks can. These thermal and mechanical loads must be dated Strength association of the heat exchanger are included and lead above all with frequent starting and stopping of the device too early voltage or Vibration breaks. To make matters worse, that outer plates of the heat exchanger package compared to the further inside lying plates due to external cooling different Are exposed to temperature fluctuations.
  • the invention has for its object to provide a steam-heated liquid heater, which is characterized by a long service life even with frequent start-up and shutdown.
  • a double wall defining a gap is arranged between each pressure plate and the outermost profile plate, and that the gap can be flowed through by a partial flow of the heat-absorbing liquid.
  • Preferred embodiments of the steam-heated liquid heater are in the Subclaims 2 to 14 specified.
  • the gap between a manifold and a collector for the heat absorbing liquid. This means that additional separate connections for feeding and discharging through the double wall coolant flowing through avoided. To that extent aimed at Structural simplification also helps if the double wall on their one End in the housing of the distributor, and at its other end in the housing of the collector protrudes.
  • the heat exchanger package is preferably one with a steam inlet and a container provided with condensate outlet, and the Liquid supply as well as the liquid discharge for the heat absorbing Liquid is sealed through the container wall.
  • the distributor and the collector for the heat absorbing Liquid inside the container are also the distributor and the collector for the heat absorbing Liquid inside the container.
  • the fatigue strength of a liquid preheater against frequent ones Load changes are not only caused by the voltages in the heat exchanger itself determined, but also by the between heat exchanger and tank adjusting thermal stresses.
  • the mechanical forces that arise here keeping it low is proposed with a preferred embodiment that in With respect to the container, one end of the heat exchanger package is fixed and the other end is arranged with play in the container.
  • the end of the heat exchanger package leading into the collector is preferably stationary, with the liquid supply line between the container wall and distributor has a longitudinally elastic line section.
  • the drawings show a container 1, which consists of a cylindrical Container casing 2, an upper hood 3 and an upper hood 4, a heat exchanger package 5 being arranged in the container 1.
  • the hoods 3, 4 are provided with several sockets.
  • D is in the upper hood 3
  • the steam can be saturated or superheated steam Act power plant turbine.
  • the hoods 3, 4 are also provided in the center with further nozzles, with a liquid supply line 6 for the liquid inlet FE and one Liquid discharge line 7 for the liquid outlet FA.
  • a liquid supply line 6 for the liquid inlet FE and one Liquid discharge line 7 for the liquid outlet FA.
  • the liquid to be warmed up enters the heat exchanger via the Liquid outlet FA leaves the heated liquid in the heat exchanger.
  • the Liquid to be heated therefore flows essentially through the container 1 along its longitudinal axis.
  • a heat exchanger package 9 is arranged almost centrally in the container 1. On the lower end of which is connected to the liquid inlet FE Distributor 10, at its upper end one with the liquid outlet FA connected collector 11.
  • the heat exchanger package 9 is a stack of plates made of profiled, d. H. deformed plates 12.
  • the individual plates 12 are designed identically and are each mirror images connected to each other to form a pair of plates. This connection is made to the Longitudinal edges of the plates, with a pair of plates between each single plates forming a wavy channel for one Medium participating in heat exchange, and an essentially tubular one Channel for the other medium participating in the heat exchange results, the both media are essentially cross-flow. Details of the Plate design of such a heat exchanger package are in the European one Patent EP 0 658 735 B1 from the same applicant.
  • the liquid to be heated therefore passes from the distributor 10 through the channels formed between the plates and into the collector 11 heated here by the steam conducted in countercurrent.
  • the steam arrives via the steam inlet D into the upper hood 3, which initially serves as a distributor, and of which on both sides in the area of the heat exchanger package 9
  • the arrows 13 recognize that the saturated or superheated steam from two each other opposite sides into the steam channels of the heat exchanger package 9 flows in. This leads to an advantageous symmetrical temperature load on the Heat exchanger package 9.
  • the steam would only enter the one-sided Incoming steam channels of the heat exchanger package, this would become one-sided high temperature load on the inflow side and thus too unfavorable Lead to temperature stresses.
  • the profiled plates 12 form an essentially cuboid plate pack, which by external pressure plates 14, which are parallel to the plates 12th extend, is held under a certain bias.
  • Preloads are tie rods 15 due to the opposite Pressure plates 14 inserted and tightened under a certain tension.
  • Figure 1 shows that the tie rod 15 outside of the profiled by Plates 12 formed cuboids.
  • FIGS 1 and 2 also show that not a continuous Printing plate is used, but each printing plate consists of a total of three Plate segments 16 composed.
  • the plate segments 16 are by a Parting line 17 running transversely to the longitudinal extent of the heat exchanger package 9 spaced. In this way, the individual plate segments 16 in expand certain limits and compensate for thermal stresses.
  • Double wall 18 is used for cooling purposes from a partial flow of heat Liquid can flow through.
  • one or more times existing inner walls 18a are provided. These are the same size and Shape like the double walls 18, divide the heat exchanger package in two or several modules, are single-walled (not flowed through) and are used for recording the tensile forces in the longitudinal direction due to the internal pressure on the liquid side. The Number is generated by the size of the tensile forces (generated by the internal pressure) Longitudinal direction determined.
  • Figure 4 shows several of the paired profile plates 12, as well the outside pressure plate 14. Between the outermost profile plate 12a and the pressure plate 14 there is a gap 19 delimiting double wall 18 Double wall 18 is in the flow direction of the heat-absorbing liquid considered longer than the profile plates 12 of the heat exchanger package, which is why Double wall 18 projects at its lower end 20 into the housing of the distributor 10. Likewise, the double wall 18 projects with its other end into the housing of the Collector.
  • the gap 19 between the two individual walls 20a, 20b Double wall 18 is approximately 2 to 5 mm with a thickness of the individual walls 20, 20b of approx. 3 mm. To ensure the thickness of the gap 19 are between the individual walls 20a, 20b extending in the flow direction Spacers 21.
  • the spacers 21 are preferably only with the outer, welded to the pressure plate 14 individual wall 20a.
  • FIG. 5 shows that the heat exchanger package 9 is in the area of FIG. 1
  • Drawn connecting edge 22 between the vapor space and liquid space is provided with wedges 23 which are welded between them in pairs Profile plates 12 protrude.
  • the wedges 23 are solidly formed from metal and both with the adjacent profile plates 12 and with the respective partition 24 to Distributor or welded to the collector.
  • FIG. 1 finally shows that the heat exchanger package 9 via webs 25th is supported against the inner wall of the container shell 2. This support takes place in the upper area of the heat exchanger package 9 at the level of the collector 11. On the other hand, there is no corresponding rigid connection between Heat exchanger package 9 and tank wall in the lower area of the tank 1. On in this way it is possible for the heat exchanger package 9 to move within the Container and expand in relation to the container. To compensate for the here adjusting length change is the liquid supply line 6 between the formed by the hood 4 container wall and the distributor 10 with a provided flexible, longitudinally elastic line section 26. The Heat exchanger package 9 including manifold 10 and collector 11 is therefore as it were hung in the container 1 and can avoid Extend thermal stress downwards unhindered.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
EP20000109947 2000-05-11 2000-05-11 Dispositif pour chauffage de liquides à la vapeur Expired - Lifetime EP1154216B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP20000109947 EP1154216B1 (fr) 2000-05-11 2000-05-11 Dispositif pour chauffage de liquides à la vapeur
DE50001791T DE50001791D1 (de) 2000-05-11 2000-05-11 Dampfbeheitzter Flüssigkeitserwärmer

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP20000109947 EP1154216B1 (fr) 2000-05-11 2000-05-11 Dispositif pour chauffage de liquides à la vapeur

Publications (2)

Publication Number Publication Date
EP1154216A1 true EP1154216A1 (fr) 2001-11-14
EP1154216B1 EP1154216B1 (fr) 2003-04-16

Family

ID=8168672

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20000109947 Expired - Lifetime EP1154216B1 (fr) 2000-05-11 2000-05-11 Dispositif pour chauffage de liquides à la vapeur

Country Status (2)

Country Link
EP (1) EP1154216B1 (fr)
DE (1) DE50001791D1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2647941A1 (fr) * 2012-04-05 2013-10-09 Alfa Laval Corporate AB Échangeur thermique à plaque
CN109578806A (zh) * 2018-12-07 2019-04-05 江苏中圣压力容器装备制造有限公司 一种lng闪蒸汽（bog）增压冷凝回收的工艺装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH296797A (de) * 1951-11-30 1954-02-28 Tech Studien Ag Plattenwärmeaustauscher für zwei Gase von erheblichem Druckunterschied.
EP0658735A1 (fr) 1993-12-18 1995-06-21 BDAG Balcke-Dürr Aktiengesellschaft Echangeur de chaleur à plaques
DE19620543A1 (de) * 1996-04-19 1997-10-23 Otto Heat Heizungs Hybrid-Plattenwärmetauscher
EP0853224A1 (fr) * 1997-01-15 1998-07-15 Balcke-Dürr GmbH Echangeur de chaleur

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH296797A (de) * 1951-11-30 1954-02-28 Tech Studien Ag Plattenwärmeaustauscher für zwei Gase von erheblichem Druckunterschied.
EP0658735A1 (fr) 1993-12-18 1995-06-21 BDAG Balcke-Dürr Aktiengesellschaft Echangeur de chaleur à plaques
DE19620543A1 (de) * 1996-04-19 1997-10-23 Otto Heat Heizungs Hybrid-Plattenwärmetauscher
EP0853224A1 (fr) * 1997-01-15 1998-07-15 Balcke-Dürr GmbH Echangeur de chaleur

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2647941A1 (fr) * 2012-04-05 2013-10-09 Alfa Laval Corporate AB Échangeur thermique à plaque
WO2013150054A1 (fr) * 2012-04-05 2013-10-10 Alfa Laval Corporate Ab Échangeur de chaleur à plaques
US10156405B2 (en) 2012-04-05 2018-12-18 Alfa Laval Corporate Ab Plate heat exchanger
CN109578806A (zh) * 2018-12-07 2019-04-05 江苏中圣压力容器装备制造有限公司 一种lng闪蒸汽（bog）增压冷凝回收的工艺装置
CN109578806B (zh) * 2018-12-07 2024-01-23 江苏中圣压力容器装备制造有限公司 一种lng闪蒸汽（bog）增压冷凝回收的工艺装置

Also Published As

Publication number Publication date
EP1154216B1 (fr) 2003-04-16
DE50001791D1 (de) 2003-05-22

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