EP1190160A1 - Element et procede pour conduire un milieu chaud soumis a une pression elevee - Google Patents

Element et procede pour conduire un milieu chaud soumis a une pression elevee

Info

Publication number
EP1190160A1
EP1190160A1 EP00940412A EP00940412A EP1190160A1 EP 1190160 A1 EP1190160 A1 EP 1190160A1 EP 00940412 A EP00940412 A EP 00940412A EP 00940412 A EP00940412 A EP 00940412A EP 1190160 A1 EP1190160 A1 EP 1190160A1
Authority
EP
European Patent Office
Prior art keywords
pressure
hot
cold
medium
component according
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Withdrawn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
EP00940412A
Other languages
German (de)
English (en)
Inventor
Detlef Haje
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.)
Siemens AG
Original Assignee
Siemens AG
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 Siemens AG filed Critical Siemens AG
Priority to EP00940412A priority Critical patent/EP1190160A1/fr
Publication of EP1190160A1 publication Critical patent/EP1190160A1/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D9/00—Stators
    • F01D9/06—Fluid supply conduits to nozzles or the like
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L7/00—Supporting of pipes or cables inside other pipes or sleeves, e.g. for enabling pipes or cables to be inserted or withdrawn from under roads or railways without interruption of traffic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L9/00—Rigid pipes
    • F16L9/18—Double-walled pipes; Multi-channel pipes or pipe assemblies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/10—Water tubes; Accessories therefor
    • F22B37/14—Supply mains, e.g. rising mains, down-comers, in connection with water tubes

Definitions

  • the invention relates to a component which is designed to guide a standing under a hot press, a hot temperature aufwei ⁇ send hot medium as well as a corresponding method.
  • Components that carry hot steam under high pressure are e.g. the pipelines between the steam turbines and the evaporator or reheater but also the steam turbine housing, the separating vessel, valves installed in the pipelines, diversion stations for load-dependent diversion of steam or also collecting vessels (not shown in more detail) for steam occurring from an overheating process.
  • EP-0 075 072 AI shows a multi-layer wall for separating different pressures, media and / or temperatures.
  • the wall shells are arranged at intervals and there are different pressures, media and / or temperatures in the interstices.
  • WO-A-99/00620 shows a high temperature flange connection.
  • a thermally stressed inner area of the high-temperature flange connection is surrounded by a cavity through which a cooling medium for cooling the high-temperature flange connection can be passed.
  • Patent Abstracts of Japan No. 07233900 describes a gas line with an inner tube and with an outer tube concentrically surrounding the inner tube.
  • a hot exhaust gas flows through the inner tube under high pressure.
  • thermal insulation consisting of two layers is provided in the annular space between the inner tube and the outer tube.
  • the thermal insulation consists of a solid thermal insulation layer, which is applied to the inner surface of the outer tube, and a static air layer in the annular space between the thermal insulation layer and the outer surface of the inner tube.
  • the pressure under which the air layer is located can be adjusted by supplying compressed air to the finger space or by letting it escape from the annular space.
  • DE 34 21 067 AI discloses a live steam inflow device for a high pressure steam turbine.
  • the inflow direction has two inlet pipes, one of which
  • Inner housing and an outer housing of the steam turbine are separable and arranged concentrically to form a space.
  • Cow steam with a lower temperature and lower pressure than the live steam in the inner inlet pipe is conducted between the inner and the outer round pipe in such a way that the difference between the pressures acting on the walls of the inner and the outer round pipe and the temperatures of the walls of the two round pipes are reduced ,
  • the cow steam is removed from a middle stage of the steam turbine as partially expanded steam by means of a removal opening and fed to the intermediate space, so that the inner inlet pipe is cooled.
  • the object of the invention is to provide a component which is particularly suitable for guiding a hot and pressurized medium.
  • Another object of the invention is to provide a method for guiding a hot and pressurized medium.
  • the object directed to a component is achieved by a component which is designed to guide a hot medium which is under hot pressure and has a hot temperature and which has a hot region and a cold region at least partially surrounding the hot region.
  • the hot area is separated from the cold area by a partition.
  • the cold region has a supply connection for supplying a cold medium that is colder than the hot medium under a cold pressure that corresponds at least to the hot pressure. Without the influence of the cold medium at the hot temperature, the partition is only pressure-bearing up to a maximum pressure, the maximum pressure being lower than the hot pressure.
  • Hot pressure is usually the pressure in the hot area and cold pressure is usually the pressure in the cold area.
  • the cold pressure in stationary operation of the component is preferably at least as high as the hot pressure.
  • the invention is based on the consideration that higher temperatures and / or higher pressures for a hot medium to be guided in a component cannot be increased arbitrarily by giving the component greater strength by increasing the pressure-bearing wall thickness.
  • metallic component walls such thick walls lead to considerable problems in production, for example when casting metallic walls and especially with expensive high-temperature-resistant materials at unacceptable costs.
  • the invention now strikes the path, which at first sight seems contradictory, to pass a further medium, namely the cold medium, likewise under considerable, usually even higher, pressure through the component.
  • the cold medium surrounds the hot region in a cold region, in which the hot medium is guided.
  • the partition separates the hot area from the cold area.
  • the cold area is in turn delimited by an outer wall. This results in a separation of functions for the tasks of
  • Partition wall and the outer wall delimiting the cold area The partition serves primarily to absorb the thermal load from the hot medium. It must have a high-temperature resistant material that can withstand the temperatures of the hot medium. However, the partition is largely relieved of the hot pressure in that the cold medium acts in the cold region with a counterpressure on the partition. The cold medium thus acts as a support medium for the partition.
  • the outer wall that delimits the cold region is suitable for taking up even higher pressure than the hot pressure, since the lower temperature of the cold medium compared to the hot medium does not impair the strength of the outer wall.
  • the outer wall can thus not only be comparatively thin but also made of a material that does not have to have high temperature resistance.
  • a cost advantage can thus be achieved on the one hand by the invention by using material savings in the partition wall and cheaper material in the outer wall.
  • the hot medium can be passed through the component at considerably higher pressure or at a considerably higher temperature while maintaining previous wall thicknesses.
  • the component is preferably connected to a safety valve in such a way that a prescribable pressure difference between the cold pressure and the hot pressure cannot be exceeded by the action of the safety valve.
  • the safety valve accordingly prevents an inadmissibly high pressure difference between the cold pressure and the hot pressure.
  • a pressure accumulator is preferably arranged in front of a valve in the hot area, which reduces the formation of a pressure surge during switching or adjusting processes of the valve.
  • the cold region is preferably connected to a pressure accumulator for the cold medium in such a way that a predeterminable, maximum speed for pressure reduction in the cold region is not exceeded. If there is a sudden drop in pressure in the
  • Cold medium for example in the event of a fault, is ensured by the pressure accumulator that the pressure in the cold medium is reduced only slowly.
  • the pressure accumulator being so ⁇ is contemplated that the speed of the drop in pressure is adjusting construction is slower than an adjustable speed for the pressure reduction in the hot medium.
  • the pressure in the hot medium can thus be reduced about as quickly or faster than the pressure in the cold medium.
  • the component preferably has a discharge connection for the cold medium that is separate from the supply connection, so that the cold medium can be continuously flowed through the cold area. With a continuous flow of cold medium through the cold area, there is no significant heating of the cold medium, which u. U. the strength of the partition or the outer wall closing the cold area was impaired.
  • the partition preferably has thermal insulation. The heat insulation reduces heat losses from the hot medium. Since the cold medium cools the partition wall, these heat losses without thermal insulation could be undesirably high compared to a conventional design without cold medium.
  • the heat insulation can, for example, be attached to the outside of the partition wall adjacent to the cold area. However, the thermal insulation can also be implemented, for example, from a coating on the inside of the partition wall, ie adjacent to the hot area, or as an intermediate layer within the partition wall.
  • the hot area is preferably designed to be movable in relation to the cold area.
  • the hot area expands considerably. This warm expansion does not exist for the cold area, since this is kept at the temperature of the cold medium.
  • suitable expansion compensators e.g. a bellows-shaped wall area in the partition, the hot area can be designed so that it can be moved so that there is no build-up of inadmissibly high thermal stresses.
  • the component is preferably designed as a pipeline, the hot region being formed by an inner tube and the cold region being formed by an outer tube.
  • the tube wall of the inner tube is thus the partition or part of the partition and the tube wall of the outer tube is an outer wall which delimits the cold region.
  • the inner tube is further preferably movably supported on the outer tube along a pipe axis.
  • a Abstutzung of the inner tube is' required. Due to the movable support along the pipeline axis, it is above mentioned heat-moving execution of the hot area compared to the cold area ensured.
  • the inner tube is stiffened against bulging, in particular by radially encircling rings. Since the partition wall, that is to say the inner tube wall, is made comparatively thin in accordance with the above statements due to the prying effect of the cold medium, stiffening of the inner tube can be advantageous. This stiffening preferably takes place by means of circumferential rings applied radially to the inner tube, which in a more preferred embodiment are embedded in thermal insulation applied to the inner tube in such a way that there is no increased flow resistance for the cold medium.
  • the component is preferably designed as a valve.
  • a complex shaped component like a valve there can be big manufacturing problems with high wall thicknesses.
  • casting the valve walls is difficult from a certain wall thickness. This problem is solved by reducing the wall thickness by dividing it into a hot area and a cold area.
  • the hot medium is preferably steam or supercritical water.
  • the cold medium is also preferably steam. It can also be water.
  • the component is preferably a component of a steam turbine system. Components of a steam turbine plant are exposed to particularly high temperatures and pressures. Expensive special steels are already being used to meet the combined requirement of high temperatures and high pressures. At metal temperatures of 620 ° C, the materials currently used (e.g. 10% chrome steel) reach their application limit and only have low strength values. For steam-carrying, pressurized components, this leads to disproportionately high wall thicknesses. As stated above, this limits the pourability of valve housings and turbine reached home. Furthermore, the high wall thickness means a large amount of material and thus high costs for pipes.
  • the component is preferably a collecting container for steam emerging from an overheating process, a steam boiler for generating or heating steam, a separating container for separating water from steam or a steam turbine house.
  • the component is preferably connected to a steam boiler in such a way that the cold medium can be fed to the steam boiler and can be converted there into the hot medium by heating.
  • the cold medium thus corresponds to the hot medium, the cold medium being fed to the heating process, while the hot medium is being removed from the heating process.
  • the hot medium that has already been heated by the boiler is enclosed by a medium that is just about to be heated.
  • the feed water to be supplied to the steam boiler as the cold medium could enclose the live steam generated in the steam boiler from the feed water as the hot medium.
  • steam to be supplied to an intermediate superheating process could cause the im
  • the cold medium is colder than the hot medium, but the cold medium also has at least ⁇ en pressure of the hot medium and can therefore serve as a supporting medium for the partition.
  • An embodiment is thus preferred in which the outer tube of a feed water pump with the steam boiler and the inner tube connects the steam boiler with a steam turbine part in terms of electrical engineering. Also preferred is an embodiment in which the outer pipe connects a steam turbine part of a first pressure area and the inner pipe connects the steam boiler to a steam part of a second pressure area, which is lower than the first pressure area.
  • the object directed to a method is achieved by a method for guiding a hot medium which is under a hot pressure and has a hot temperature in a hot region, the hot region being flowed around by a cold medium which has a lower temperature than the hot medium and a cold pressure which cold pressure is at least half the hot pressure.
  • the cold pressure is preferably at least as large as the hot pressure.
  • FIG. 1 shows a steam turbine system according to the prior art
  • FIG. 2 shows a steam turbine system with components for guiding hot steam, which are surrounded by colder supporting steam
  • FIG. 3 shows a cross section through a pipeline with an inner and outer tube
  • FIG. 4, 5 shows an inner tube corresponding to FIG 6 different execution of a thermal insulation
  • FIG. 6 a pipeline with a stiffened inner tube with a longitudinal section
  • FIG. 7 shows an inner tube in a longitudinal section with bellows-shaped expansion compensator, 8, 9 an inner tube with a movable seal, FIG. 10-12 a pipeline with a cross section with a supported inner tube, FIG. 13 a section of an axially movable inner tube support,
  • FIG. 14 shows a cross section through flow-wise designed inner tube supports
  • FIG. 16 shows an axially fixed inner tube support
  • FIG. 17 shows a section through the inner tube support of FIG. 16
  • FIG. 18 shows a pipeline with inner pipe and outer pipe, supports and expansion compensators
  • FIG 19 shows a right-angled pipe with inner pipe and outer pipe
  • FIG. 20 shows a branched pipe with inner and outer pipe
  • FIG. 21 shows a superheater outlet collector in cross section
  • 23 shows a view of the pipe feed line from FIG. 22,
  • FIG. 24 shows another embodiment of the pipe feed line of a superheater outlet collector
  • FIG. 25 shows a heat-mobile version of a superheater outlet collector in longitudinal section
  • FIG. 26 shows a steam turbine valve in longitudinal section
  • FIG. 27 shows a high-pressure steam turbine in longitudinal section.
  • FIG. 1 shows a steam turbine system 80.
  • a feed water tank 18 is connected to two feed water pumps 19 connected in parallel and one feed water pump 19 each following check valve 20.
  • the following lines are brought together behind the non-return flaps 20 as feed water lines 23.
  • the feed water line 23 leads to a high pressure preheater 21 before and after the flow High-pressure preheaters 21 bypass valves 22 are arranged, with which bypassing the high-pressure preheater 21 is possible.
  • the high-pressure preheater 21 is connected to the evaporator and economizer heating surfaces 1.
  • the evaporator and economizer heating surfaces 1 are connected to live steam superheater heating surfaces 2.
  • the live steam superheater heating surfaces are connected to a live steam superheater outlet collector 3.
  • a live steam line 4 leads to a live steam valve 5 and to a high-pressure bypass station 24.
  • a line leads to a high-pressure turbine 6.
  • a cold intermediate superheating line 7 leads to intermediate superheater heating surfaces 8.
  • the intermediate superheater heating surfaces 8 are also included connected to a reheater outlet collector 9.
  • the trap valve 11 is connected to a medium-pressure tower 12.
  • An overflow line 13 leads from the medium-pressure turbine 12 to a low-pressure turbine 14.
  • a line also leads from the low-pressure bypass station 25 to the low-pressure turbine 14.
  • the low-pressure turbine 14 is also connected to a condenser 15.
  • the condenser 15 is connected to a condensate pump 16.
  • the condensate pump 16 is connected to a low-pressure preheater 17.
  • the low pressure preheater 17 is connected to the feed water tank 18.
  • feed water from the feed water tank 18 is fed to the high-pressure preheater 21 via the feed water pumps 19 and preheated there.
  • the feed water preheated in this way is fed via the feed water line 23 to the evaporator and economizer heating surfaces 1 and the heating steam superheater 2 and heated there.
  • Generated steam or supercritically heated water collects in the superheater device collector 3. The generated one
  • Live steam is fed to the high-pressure turbines 6 via the live steam line 4.
  • the emerging from the high pressure turbine 6 M ro P 1 P 1
  • FIG. 2 shows a steam turbine system 80 corresponding to FIG. 1, but a completely new concept is used for the components which are particularly exposed to pressure and temperature.
  • the live steam line 4 is designed as an inner tube in an outer tube (see FIG. 3), the outer tube forming the feed water line 23.
  • the hot reheater line 10 is an inner tube which is surrounded by the cold reheater line 7 as an outer tube. This design turns a hot medium, such as live steam or reheated steam, from a cold medium, for example
  • the cold medium has a higher pressure than the hot medium.
  • the respective inner tube can be designed with a thin wall thickness, since the respective cold medium serves as a supporting medium that prongs the inner tube.
  • the wall of the respective outer tube can also be made thinner or from a comparatively cheap material, since there is no impairment of strength due to a high temperature.
  • the superheater outlet collectors 3, 9 or valves 5, 11 or the bypass stations 24, 25 are designed such that the hot medium to be conveyed is surrounded by a cold medium.
  • injection nozzles 29 for injecting water for further cooling of the cold medium are provided at suitable points.
  • the Uberhitzeraus ⁇ outlet manifold 3, 9, the diversion stations 24, 25 and the valves 5, 11 are each provided with a drain 28 for the cold medium, so that a defined flow for the cold medium can be set.
  • the outer tubes, that is to say the feed water line 23 or the cold reheater line 7, are each provided with a pressure accumulator 30 for the cold medium, so that there is no sudden drop in pressure in the cold medium > L to to PP 1
  • FIG. 4 shows another embodiment for the heat insulation 68 of the inner tube 70.
  • the heat insulation 68 is in this case designed as an inner coating of the inner tube 70.
  • Another conceivable embodiment for the arrangement of the heat insulation 68 is shown in FIG. 5.
  • the heat insulation 68 is integrated as an intermediate layer within the wall of the inner tube 70.
  • FIG. 6 shows a longitudinal section of an inner tube 70, which is surrounded by thermal insulation 68.
  • the inner tube 70 is surrounded by radial circumferential stiffening rings 74. In this way, buckling can be avoided despite the comparatively thin design of the inner tube 70.
  • the stiffening arms 74 are integrated into the thermal insulation 68, so that there is no increased flow resistance for the cold medium 61 flowing past.
  • FIGS. 7 to 9 each show a longitudinal section of an inner tube 70 which is provided with means for absorbing thermal expansion.
  • the inner tube 70 is integrated in a bellows-shaped expansion compensator 200 m in FIG.
  • heat-movable seals 206 m are arranged in axially directed and radially circumferential grooves 204.
  • Holding elements 207 each hold the sealing elements 206 on a side opposite the grooves 204. Due to a split design of the inner tube 70, this can expand due to warm conditions, a seal being provided by the sealing elements 206 which are movable in the grooves 204.
  • FIGS. 10 to 12 each show a pipeline 62 formed from an inner tube 70 and an outer tube 72 in a cross section.
  • the inner tube 70 is opposite to that Outer pipe 72 is supported to accommodate any pipe forces or the weight of the inner pipe 70 and to adjust the vibration behavior of the pipeline 69.
  • support elements 300 are held in guide elements 302 in such a way that an axial and radial warm movement is made possible.
  • the embodiment according to FIG. 12 being particularly preferred with regard to the low flow resistance.
  • FIG. 13 shows an enlarged inner tube support with a support element 300, which is held in a guide element 302.
  • FIGS. 14 and 15 show a section perpendicular to the support element 300 in terms of flow technology for the guide elements 302.
  • FIG. 17 shows an embodiment which is favorable in terms of flow technology for the inner tube projection 320.
  • FIG. 18 shows a longitudinal section of a section of a pipeline 69, which is formed from an inner tube 70 and an outer tube 72.
  • the inner tube 70 is supported with supports 300 against the outer tube 72 and axially fixed at a fixing point 318.
  • Elongation compensators 200 in the inner tube 70 allow the inner tube 70 to be heated in relation to the outer tube 72.
  • FIG. 19 shows a longitudinal section through a pipe 69 bent at right angles.
  • the starting point 500 of the thermal expansions of the pipe 69 is in the region of its maximum curvature.
  • a branching pipeline 69 is shown in a longitudinal section in FIG. 20.
  • the starting point 500 of the thermal expansions here is the branching point.
  • FIG. 21 shows a cross section through an overheat outlet collector 3.
  • An inner container 601 forms a hot region 54 and is surrounded by a cold region 56, which is formed by an outer container 603.
  • FIG. 22 shows a detail of a pipeline attachment 600.
  • Superheated steam is led into the hot area 54 via a line section 602.
  • the line section 602 is delimited by an inner wall 608.
  • An outer wall 604 leads the cold region 56 beyond the inner wall 608.
  • a possible production could be carried out by welding an attachment 606 along the weld seam A to the inner wall 608 and then welding on half-shells D and C (see FIG. 23) for the outer wall 610.
  • FIG. 24 shows another manufacturing possibility in which the adapter 606 is screwed on by means of screw connections 620.
  • the sealing between the hot area 54 and the cold area 56 takes place by means of an axially mountable seal 622 which permits a warm movement.
  • FIG. 25 a heat-moving construction for a superheater collecting container 3 is shown in a longitudinal section.
  • FIG. 26 shows a steam turbine valve 5 in a longitudinal section.
  • the steam turbine valve 5 is formed from a quick-closing valve 704 and a control valve 706.
  • a valve stem 700 opens and closes the quick-closing valve 704 with respect to the quick-closing valve seat 710.
  • a valve stem 708 opens and closes the control valve 706 with respect to a control valve seat 712.
  • superheated steam 54 passes through the opened quick-closing valve 704 to the control valve 706 and, depending on the degree of opening Control valve 706 via a discharge line 716 from the steam turbine valve 5.
  • the feed area of the steam turbine valve 5 is double-walled in such a way that a hot area 54 for the superheated steam 51 is enclosed by a cold area 56 for a cold medium, in particular steam.
  • a hot area 54 for the superheated steam 51 is enclosed by a cold area 56 for a cold medium, in particular steam.
  • a discharge 28 for the cold medium can advantageously be connected to a further steam turbine part in such a way that cooling results for this steam turbine part.
  • a certain amount of the surrounding medium is continuously removed from the enclosure via the discharge 28 and introduced into the area of the further steam turbine component (not shown) to be cooled.
  • the lead out of the enclosure must be designed so that stagnation of the cold medium can be excluded.
  • FIG. 27 shows a longitudinal section of a high-pressure steam tower 6.
  • An outer housing 804 encloses an inner housing 802. Between the inner housing 802 and the outer housing 804 there remains a gap 803, which is introduced into the cold medium.
  • the cold medium has a higher pressure than superheated steam, which is guided in the inner housing 802 and sets a shaft of 808 m rotation by means of a not shown blading. This creates a support effect for the inner housing 802, which means that it can be made thinner.
  • the outer housing 804 can be manufactured with thin walls and / or from less expensive material.
  • a quick opening of a throttled control valve leads to a pressure drop in the line in front. If the design of the enclosed line is determined by this drop in load, the pressure drop in the vicinity of the valve can be provided to slow down the drop in pressure. This measure is also advantageous for the load case of a draughty partial closing of a valve.
  • injection cooling i.e. by injecting water into the steam
  • injection cooling is both possible for a central device in the high pressure steam flow as well as locally in front of the respective protected objects. It is also conceivable to use the (anyway existing) high-pressure bypass station for cooling; in the event of low load, this could be opened somewhat, and the steam that passed through could be cooled down by water injection.
  • High-pressure steam can be used to cool the entire steam. After admixing to the high-pressure steam, the entire steam can be cooled; after the admixture, lines can branch off to the protective objects.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Control Of Turbines (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)

Abstract

L'invention concerne un élément servant à conduire un milieu chaud (50) présentant une température élevée et soumis à une pression à chaud. Une zone froide (56) de l'élément entoure une zone chaude (54) dans laquelle le milieu chaud (50) est conduit. Dans la zone froide (56) est conduit un milieu froid (61) soumis à une pression égale à au moins la moitié de la pression à chaud, et de préférence soumis à une pression égale ou à une pression supérieure. On obtient ainsi une décharge d'une paroi de séparation (58) séparant la zone froide (56) de la zone chaude (54) et ainsi, globalement, un élément ayant des épaisseurs de paroi comparativement faibles.
EP00940412A 1999-06-30 2000-06-28 Element et procede pour conduire un milieu chaud soumis a une pression elevee Withdrawn EP1190160A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP00940412A EP1190160A1 (fr) 1999-06-30 2000-06-28 Element et procede pour conduire un milieu chaud soumis a une pression elevee

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP99112453 1999-06-30
EP99112453 1999-06-30
EP00940412A EP1190160A1 (fr) 1999-06-30 2000-06-28 Element et procede pour conduire un milieu chaud soumis a une pression elevee
PCT/EP2000/006031 WO2001002702A1 (fr) 1999-06-30 2000-06-28 Element et procede pour conduire un milieu chaud soumis a une pression elevee

Publications (1)

Publication Number Publication Date
EP1190160A1 true EP1190160A1 (fr) 2002-03-27

Family

ID=8238458

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00940412A Withdrawn EP1190160A1 (fr) 1999-06-30 2000-06-28 Element et procede pour conduire un milieu chaud soumis a une pression elevee

Country Status (4)

Country Link
EP (1) EP1190160A1 (fr)
JP (1) JP2003503635A (fr)
CN (1) CN1365422A (fr)
WO (1) WO2001002702A1 (fr)

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EP1744017A1 (fr) * 2005-07-14 2007-01-17 Siemens Aktiengesellschaft Turbine combinée à vapeur et procédé de fonctionnement d'une turbine combinée à vapeur
DE102010029273B4 (de) 2010-05-25 2012-10-31 Technische Universität Dresden Hochtemperaturfluidtransportsystem
CN102966806A (zh) * 2011-08-28 2013-03-13 黑利福卡斯有限公司 流体传输组件
JP6004947B2 (ja) * 2013-01-08 2016-10-12 三菱日立パワーシステムズ株式会社 蒸気タービン
CN109654911A (zh) * 2018-12-06 2019-04-19 上海发电设备成套设计研究院有限责任公司 一种夹层流体冷却的630℃~650℃的主蒸气管道
CN109506052B (zh) * 2018-12-10 2024-03-12 上海发电设备成套设计研究院有限责任公司 一种夹层承压与隔热的640℃至650℃高温蒸汽管道
CN113324600B (zh) * 2021-04-21 2022-09-20 广西电网有限责任公司电力科学研究院 一种fcb功能火电机组旁路容量测试方法

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CN1365422A (zh) 2002-08-21
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