EP0084846B1 - Exchangeur de chaleur pour une installation comportant une chaudière à vapeur surchauffée - Google Patents

Exchangeur de chaleur pour une installation comportant une chaudière à vapeur surchauffée Download PDF

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Publication number
EP0084846B1
EP0084846B1 EP83100408A EP83100408A EP0084846B1 EP 0084846 B1 EP0084846 B1 EP 0084846B1 EP 83100408 A EP83100408 A EP 83100408A EP 83100408 A EP83100408 A EP 83100408A EP 0084846 B1 EP0084846 B1 EP 0084846B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
container
exchanger according
condensate
recirculation
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.)
Expired
Application number
EP83100408A
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German (de)
English (en)
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EP0084846A1 (fr
Inventor
Karl August Jacob
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.)
Jacob Karl August
Original Assignee
Jacob Karl August
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
Priority claimed from DE3202144A external-priority patent/DE3202144C2/de
Priority claimed from DE19823213165 external-priority patent/DE3213165A1/de
Priority claimed from DE19823224153 external-priority patent/DE3224153A1/de
Priority claimed from DE19823248785 external-priority patent/DE3248785A1/de
Application filed by Jacob Karl August filed Critical Jacob Karl August
Publication of EP0084846A1 publication Critical patent/EP0084846A1/fr
Application granted granted Critical
Publication of EP0084846B1 publication Critical patent/EP0084846B1/fr
Expired legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • 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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/04—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being spirally coiled
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
    • F22D1/00—Feed-water heaters, i.e. economisers or like preheaters
    • F22D1/16—Feed-water heaters, i.e. economisers or like preheaters with water tubes arranged otherwise than in the boiler furnace, fire tubes, or flue ways
    • F22D1/18—Feed-water heaters, i.e. economisers or like preheaters with water tubes arranged otherwise than in the boiler furnace, fire tubes, or flue ways and heated indirectly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22D—PREHEATING, OR ACCUMULATING PREHEATED, FEED-WATER FOR STEAM GENERATION; FEED-WATER SUPPLY FOR STEAM GENERATION; CONTROLLING WATER LEVEL FOR STEAM GENERATION; AUXILIARY DEVICES FOR PROMOTING WATER CIRCULATION WITHIN STEAM BOILERS
    • F22D11/00—Feed-water supply not provided for in other main groups

Definitions

  • the invention relates to a heat exchanger for operating a superheated steam boiler system, for example for dry cleaning, laundries or the like, consisting of a container with connections for the supply and discharge of a first medium flowing through the container and with one arranged in the container over its height extending, through which a second medium can flow, with connections opening into a cover of the container for a feed line and a discharge line, the feed line extending to the lowest point of the spiral and the discharge line starting from the highest point of the spiral.
  • Every steam boiler system is provided with a condensate return.
  • the condensate consists of a mixture of vapor at approx. 105 ° C and a condensed hot steam mixture of approx. 90-100 ° C.
  • the hot condensed water is normally collected in a condensate container in the boiler system.
  • a boiler feed water pump then presses this hot water back into the superheated steam boiler, where evaporation takes place again. Since water above 80-85 ° C causes difficulties for the pumps, either the condensate container is made very large or the condensate is additionally cooled. On the other hand, however, this leads to difficulties again if the condensate is too cold (e.g. 60 ° C), since then the boiler heating surfaces or pipes will rot.
  • the invention is therefore based on the object to provide a heat exchanger with which the heat of the condensate of a steam boiler system can be optimally used to increase the temperature of the feed water, the highest possible energy savings can be achieved for the operation of the steam boiler and in a simple manner to different Operating conditions or different sizes of the high-pressure steam boiler, for example higher output, shortening the heating time of the boiler, can be easily adapted and the output of the heat exchanger can also be controlled depending on the amount of condensate.
  • connection for the supply of the first medium is also provided in the lid of the container, that the spiral arranged vertically in the container is formed at its upper end as a flat spiral that in Container is a baffle plate extending from the lid, reaching to the level of the flat spiral, through which the vapor of the first medium can be guided to the locations of the spirals that are located at the heat exchanger inlet and that a recirculation plate is provided below the flat spiral to increase the length of time of the first Enlarge medium in the area of the flat spiral.
  • the recirculation plate provided below the flat spiral according to the invention has the essential advantage that the hot fresh condensate develops intensive turbulence in the area of the flat spiral and releases a greater part of its heat content to the flat spiral.
  • the inflowing fresh condensate evaporates, initially flows around the flat spiral on all sides and hits the recirculation plate, which results in the strong turbulence.
  • the heat exchanger according to the invention is connected in the condensate circuit after the feed water pump and before the boiler inlet.
  • This design has the advantage that the hot fresh condensate is cooled and, on the other hand, the boiler feed water is heated from about 60 ° C in the feed water spiral through the fresh condensate to about 90-95 ° C and also higher, before the boiler enters.
  • the condensate line is connected to consumers and leads to a feed water container, the feed water supply line being connected to a pump and the feed water discharge line being connected to a high-pressure steam boiler.
  • the feed water spiral is flat at its upper end according to a first embodiment or, according to modifications, upwards cav or convex.
  • the heat content of the condensate that is present in the fresh condensate is optimally utilized.
  • the recirculation plate is advantageously arranged on the feed water supply line.
  • the recirculation plate is flat.
  • the recirculation plate is concave towards the cover.
  • the recirculation plate is convex toward the cover.
  • the bottom of the heat exchanger can also act as recirculation plates.
  • this can be profiled according to a further feature of the invention.
  • the profiling can be carried out by means of elevations or depressions, which can be point-shaped or linear.
  • the diameter of the recirculation plate is preferably chosen to be smaller than the inside diameter of the container.
  • the vapor vapor thus flows approximately radially outward from the center of the heat exchanger and downward between the recirculation plate and the wall of the heat exchanger.
  • the recirculation plate is arranged in a height-adjustable manner in yet another embodiment of the invention.
  • the invention provides that at least one pipe section arranged between the container and the lid with a second flat spiral, a second baffle plate and a second recirculation plate and connecting means for the supply lines and discharge lines between the pipe section and the container are provided.
  • This inventive design of additionally attachable pipe sections with flat spiral advantageously enables simple adaptation to different operating sizes of the high-pressure steam boiler to be operated in each case.
  • the z. B. second recirculation plate in the pipe section be formed analogously to the recirculation plate in the heat exchanger tank itself.
  • the z. B. second recirculation plate arranged on the feed water supply line of the pipe section.
  • the recirculation plate is flat.
  • the diameter of the recirculation plate is smaller than the inside diameter of the pipe section.
  • the diameter of the recirculation plate is larger than the free inner diameter of the baffle plate.
  • the or one of the recirculation plates can be arranged to be height-adjustable.
  • Drive means for height adjustment means (des) of the recirculation plates (s) are advantageously provided.
  • the drive means for the height adjustment means can be controlled electrically or electronically.
  • the recondensate is separated from the consumption points in two aggregate states, gas and liquid, namely vapor and hot water.
  • the formation of steam in the specially shaped primary zone gives a high k value.
  • the boiler feed water is preheated in the secondary zone. This zone is located in the lower third of the heat exchanger, namely in the liquid area.
  • a non-return valve is arranged in the condensate line from the heat exchanger to the condensate container.
  • the configuration according to the invention ensures that a dynamic pressure which ensures the function of the heat exchanger is created.
  • the heat exchanger works in the pressure range of ⁇ 0.2 bar, the non-return flap prevents the condensate that is used up from being thermally sucked back.
  • the heat exchanger according to the invention can also be used to produce process water.
  • a process water container jacket is arranged around the heat exchanger with a process water supply connection and a process water discharge connection.
  • the condensate line in the container is thermally insulated.
  • a high-pressure steam boiler system is shown schematically.
  • Such a system comprises a high-pressure steam boiler 1, which emits a high-pressure steam at a temperature of approximately 150-170 ° C. at a pressure of approximately 5-7 bar.
  • the superheated steam is supplied to 2 consumers 3 ', 3 ", 3"' via a high-pressure steam line.
  • Such consumers can be, when using the boiler system in a chemical cleaning or in a laundry, ironing machines, steaming dolls, steam booths or the like.
  • the hot condensate is returned from the consumers 3 ', 3 ", 3"' via a first condensate line 4.
  • This line 4 normally leads to a feed water (condensate) container 5, in which the condensate cools. From the condensate tank 5, the feed water is fed back to the high-pressure steam boiler 1 by means of a feed water pump 7.
  • the condensate is passed through a heat exchanger 8 according to the invention before it enters the condensate container 5.
  • the heat of the condensate flowing back at a temperature of approximately 90-105 ° C. is passed to the feed water dispensed so that the condensate has a temperature of about 50 ° C when leaving the heat exchanger 8 and enters the feed water tank 5 at this temperature. Due to the cooling in the container 5, the temperature of the feed water after the pump 7 drops to about 40 ° C.
  • the temperature of the boiler water is then increased again to about 80-105 ° C. Since the feed water already enters the steam boiler 1 at a relatively high temperature, the amount of heat required to generate the steam at 150-170 ° C. is reduced. Measurements have shown that at least 20% less heating energy is required.
  • This heat exchanger 8 generally consists of a cylindrical vessel with a cover part 17, into which the condensate line 4 and a feed water supply line 6 open.
  • the cooled condensate is led to a feed water tank 5 by means of a second condensate line 10.
  • the feed water supply line 6 extends from the cover 17 to the lowest point of the heat exchanger 8 and is then guided in a spiral as a coil to a feed water discharge line 9 also arranged on the cover 17.
  • the arrangement of the condensate line 4 on the cover 17 ensures that the hottest condensate strikes the end turns of a feedwater spiral 11 shortly before it exits the heat exchanger 8.
  • a further increase in the temperature of the pumped-through boiler feed water can be achieved in that the feed water spiral 11 is provided at its upper end with an additional, flat or upwardly convex or concave feed water spiral 12 or flat spiral.
  • a baffle plate 16 force jet plate
  • This baffle plate 16 can be disc-shaped or annular. The vapor vapor is guided through this baffle plate 16 to the locations of the spirals 11 and 12, which are located at the heat exchanger inlet.
  • the use of a flat flat spiral 12 and a baffle plate 16 results in a further increase in the temperature of the boiler feed water by approximately 5 ° C.
  • a recirculation plate 18 is provided below this flat spiral 12.
  • This, preferably round, recircula tion plate 18 is suitably arranged on the feed water supply line 6.
  • the recirculation plate 18 can be welded to the line 6. It can also be placed or suspended on suitable webs 19.
  • the recirculation plate 18 can also be arranged to be height-adjustable. This results in the possibility of adapting the gap between the baffle plate 16 and the recirculation plate 18 to the respective throughput of fresh condensate.
  • the training is such that the diameter of the recirculation plate 18 is smaller than the inner diameter of the heat exchanger. This results in a gap between the jacket of the heat exchanger and the recirculation plate 18, through which the cooled condensate can sink downward.
  • the recirculation plate 18 can, as shown in FIG. 4 on the left, be flat or also convex or concave in the direction of the cover 17, as shown in FIG. 4 on the right.
  • FIG. 5 the assignment of the individual lines and spirals as well as the baffle plate 16 and the recirculation plate 18 can be seen in a cross section along the line I-I of FIG. 4 in the plane of the flat spiral 12.
  • a second heat exchanger is arranged on the container 8 of the heat exchanger in order to adapt to the respective output of the high-pressure steam boiler 1 (FIG. 6) in such a way that there is a pipe section 20, pipe section 20 and container 8 are connected to one another via ring flanges 22, 23.
  • 7 shows such a heat exchanger 8 according to the invention in connection with the pipe section 20 in longitudinal section.
  • the additional heat exchanger section provided according to the invention is arranged in a pipe section 20.
  • This pipe section 20 is provided with an upper ring flange 21, to which a cover 17 is connected.
  • the condensate line 4 and a feed water supply line 6 ′′ open into the cover part 17.
  • the feed water is returned to the boiler 1 through a feed water discharge line 9 ′′ likewise arranged on the cover 17.
  • the cooled condensate is conducted to a feed water container 5 by means of a condensate line 10 arranged on the container 8.
  • the arrangement of the condensate line 4 on the cover 17 ensures that the hottest condensate strikes the end turns of a feedwater flat spiral 12 "arranged in the pipe section 20, shortly before it emerges from the heat exchanger pipe section 20.
  • the feedwater spiral 11 is also formed in the container 8 at its upper end as a flat or concave or convex feedwater flat spiral 12 ', which is connected to a flat spiral 12 "in the pipe section 20.
  • a recirculation plate 18" is also provided in the pipe section 20, and a baffle plate 16 ".
  • the feed water spiral 11 or the approximately flat feed water flat spirals 12 ′ and 12 ′′ are shown inclined in FIG. 7, deviating from the actually approximately horizontal position in the container 8 or in the pipe section 20.
  • This use of flat flat spirals 12 ', 12 "and baffle plates 16', 16” results in a further increase in the temperature of the boiler feed water by approximately 5 ° C.
  • the recirculation plates 18 ', 18 "provided below the flat spiral 12' or 12" increase the residence time of the vapor in the area of the flat spirals 12 'or 12 ".
  • each recirculation plate 18 ', 18 is expediently each arranged on the feed water supply line 6' or 6".
  • the respective recirculation plate 18 'or 18 can be welded to the line 6' or 6". It can also be placed or suspended on suitable webs 19.
  • each recirculation plate 18 'or 18 can also be arranged in a height-adjustable manner. This results in the possibility of adapting the gap between the associated baffle plate 16' or 16" and the recirculation plate 18 ', 18 "to the respective throughput of vapor adapt.
  • the training can be such that height adjustment means 25 are provided which are actuated by drive means 26.
  • the drive means 26 can be controlled by electronic or electrical elements which control the drive means 26 depending on the amount of vapor generated.
  • a turbine can be provided on the condensate line 4 for measuring the amount of the incoming vapor or condensate.
  • the formation of the recirculation plates 18 'or 18 " can be such that their diameter is smaller than the inside diameter of the container 8 or the pipe section 20. This results in a gap between the casing of the container 8 or pipe section 20 and the recirculation plate 18 'or 18 ", through which the cooled condensate can sink downwards.
  • the respective recirculation plate 18 ′, 18 ′′ can, as shown in FIG. 7, be flat or also convex or concave in the direction of the cover 17.
  • the additional heat exchanger part in the pipe section 20 makes it possible to adapt the heat exchanger to the respective operating conditions of the associated high-pressure steam boiler or the system.
  • the feed water line 6 'or 6 "of the individual pipe sections 20 and the heat exchanger part 8 are connected to one another by any connecting means 24 known per se.
  • Fig. 8 is in a cross section along the lines I-1 and 11-11 of Fig. 7 in the planes of the flat spirals 12 ', 12 "the assignment of the individual lines and spirals and the baffle plates 16', 16" and Recirculation plates 18 ', 18 "can be seen.
  • FIG. 9 shows a heat exchanger 8 which is further developed according to the invention.
  • FIG. 10 shows this heat exchanger 8 according to the invention in longitudinal section.
  • the cooled condensate is fed to the feed water tank 5 by means of a second condensate line 10.
  • the second condensate line 10 leading upwards has a length of approximately 2.5 m and is preferably provided with a non-return valve 27 in the upper region.
  • the arrangement of the check valve 27 in the line 10 ensures that when the heat exchanger 8 is working in the negative pressure region, the thermally used condensate is not sucked back into the heat exchanger 8 and the gas volume of the primary zone is maintained.
  • the dynamic pressure which is advantageous for the function of the heat exchanger is created.
  • the resulting subdivision of the heat exchanger into two zones enables the condensate that occurs to suddenly relax, i.e. H. expands and increases to a gas volume in the sense of the state of aggregation as gas.
  • a large part of the heat content is suddenly withdrawn from the gas volume by contact with a large heat-absorbing surface, namely the feedwater spiral 11.
  • the steam collapses to approx. 1/1000 of its volume, creating a vacuum of up to -0.4 bar in the entire condensate line system. This accelerates the condensate to the heat exchanger.
  • the repulsive mode of operation of the heat exchanger in the plus and minus pressure range enables the pressure zone to be set up and thus the storage of uneven fresh condensate. Since the dynamic pressure principle, raising the condensate line on the outlet side by approx. 2.5 m, creates a pressure with a maximum of approx. 0.4 bar, the primary zone can sometimes be compared to a low-pressure steam boiler.
  • a further utilization of the heat content of the condensate can take place in that the heat exchanger 8 is surrounded by an additional jacket 15 (FIG. 2 or 3) which forms a process water tank.
  • the process water can be supplied through a process water supply connection 13 and can be removed from the process water cylinder through a process water discharge line 14.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Water Supply & Treatment (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Exhaust Gas Treatment By Means Of Catalyst (AREA)
  • Treating Waste Gases (AREA)

Claims (17)

1. Echangeur de chaleur pour l'exploitation d'une installation comprenant une chaudière à vapeur surchauffée, par exemple pour des entreprises de nettoyage à sec, des laveries ou analogues, comprenant un récipient (8) avec des raccords pour l'amenée et.l'évacuation d'un premier fluide, traversant le récipient, et un serpentin (11), placé dans le récipient, s'étendant sur la hauteur de celui-ci et pouvant être parcouru par un second fluide, avec des raccords débouchant dans un couvercle (17) du récipient pour une conduite d'amenée (6) et une conduite d'évacuation (9), la conduite d'amenée s'étendant jusqu'au point le plus bas du serpentin et la conduite d'évacuation partant du point le plus haut du serpentin, caractérisé en ce que le raccord pour l'amenée du premier fluide est également prévu dans le couvercle (17) du récipient, que le serpentin (11), disposé verticalement dans le récipient, est réalisé à son extrémité supérieure sous la forme d'un serpentin plat (12), qu'une chicane (16) partant du couvercle (17) s'étend dans le récipient (8) jusqu'au plan du serpentin plat (12), chicane par laquelle la buée du premier fluide peut être amenée aux points des serpentins (11, respectivement 12) qui sont situés à l'entrée de l'échangeur de chaleur, et qu'une tôle de recyclage (18) est prévue au-dessous du serpentin plat (12) afin de prolonger la durée de séjour du premier fluide dans la région du serpentin plat (12).
2. Echangeur selon la revendication 1, caractérisé en ce que le serpentin plat (12) est plan.
3. Echangeur selon la revendication 2, caractérisé en ce que le serpentin plat (12) possède une courbure concave ou convexe dirigée vers le haut.
4. Echangeur selon la revendication 3, caractérisé en ce que la tôle de recyclage (18) est disposée sur la conduite d'amenée (6).
5. Echangeur selon la revendication 3 ou 4, caractérisé en ce que la tôle de recyclage (18) est plane.
6. Echangeur selon la revendication 3 ou 4, caractérisé en ce que la tôle de recyclage (18) possède une courbure concave dirigée vers le couvercle (17).
7. Echangeur selon la revendication 3 ou 4, caractérisé en ce que la tôle de recyclage (18) possède une courbure convexe dirigée vers le couvercle (17).
8. Echangeur selon une des revendications 3 à 7, caractérisé en ce que la tôle de recyclage (18) est profilée.
9. Echangeur selon une des revendications 3 à 8, caractérisé en ce que le diamètre de la tôle de recyclage (18) est plus petit que le diamètre intérieur du récipient (8).
10. Echangeur selon une des revendications 3 à 9, caractérisé en ce que la tôle de recyclage (18) est réglable en hauteur.
11. Echangeur selon une des revendications 3 à 10, caractérisé par au moins une section de tuyau (20) disposée entre le récipient (8) et le couvercle (17) et comprenant un deuxième serpentin plat (12'), une deuxième chicane (16') et une deuxième tôle de recyclage (18'), ainsi que par des moyens de liaison (24) pour les conduites d'amenée (6', 6") et les conduites d'évacuation (9', 9") entre la section de tuyau (20) et le récipient (8).
12. Echangeur selon la revendication 11, caractérisé en ce que la deuxième tôle de recyclage (18') est disposée sur la conduite d'amenée (6') de la section de tuyau (20).
13. Echangeur selon la revendication 11 ou 12, caractérisé en ce que le diamètre de la deuxième tôle de recyclage (18') est plus petit que le diamètre intérieur de la section de tuyau (20).
14. Echangeur selon une des revendications 11 à 13, caractérisé en ce que le diamètre de la tôle de recyclage (18 respectivement 18') est plus grand que le diamètre intérieur libre de la chicane (16 respectivement 16').
15. Echangeur selon une des revendications 11 à 14, caractérisé en ce que l'une au moins des tôles de recyclage (18 respectivement 18') est réglable en hauteur.
16. Echangeur selon la revendication 15, caractérisé par des moyens d'entraînement (16) pour des moyens de réglage en hauteur (25) de la tôle de recyclage (18 respectivement 18'). 17. Echàngeur selon une des revendications 1 à 16, caractérisé par une enveloppe ou double paroi à eau industrielle (15), qui entoure le récipient (8) et présente un raccord d'amenée d'eau industrielle (13) et un raccord d'évacuation d'eau industrielle (14).
EP83100408A 1982-01-23 1983-01-19 Exchangeur de chaleur pour une installation comportant une chaudière à vapeur surchauffée Expired EP0084846B1 (fr)

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
DE3202144A DE3202144C2 (de) 1982-01-23 1982-01-23 Wärmetauscher zum Betrieb eines Hochdruck-Dampfkessels
DE3202144 1982-01-23
DE3213165 1982-04-08
DE19823213165 DE3213165A1 (de) 1982-04-08 1982-04-08 Waermetauscher zum betrieb eines hochdruck-dampfkessels
DE19823224153 DE3224153A1 (de) 1982-06-29 1982-06-29 Waermetauscher zum betrieb eines hochdruck-dampfkessels
DE3224153 1982-06-29
DE3248785 1982-12-31
DE19823248785 DE3248785A1 (de) 1982-12-31 1982-12-31 Waermetauscher zum betrieb eines hochdruck-dampfkessels

Publications (2)

Publication Number Publication Date
EP0084846A1 EP0084846A1 (fr) 1983-08-03
EP0084846B1 true EP0084846B1 (fr) 1987-12-02

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EP83100408A Expired EP0084846B1 (fr) 1982-01-23 1983-01-19 Exchangeur de chaleur pour une installation comportant une chaudière à vapeur surchauffée

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US (1) US4550687A (fr)
EP (1) EP0084846B1 (fr)
JP (1) JPS59500064A (fr)
KR (1) KR840003346A (fr)
AT (1) ATE31218T1 (fr)
AU (1) AU1151183A (fr)
DE (1) DE3374807D1 (fr)
ES (1) ES519175A0 (fr)
PT (1) PT76131B (fr)
WO (1) WO1983002658A1 (fr)

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HU195687B (en) * 1985-06-07 1988-06-28 Energiagazdalkodasi Intezet Apparatus for superpressure steam systems for supplying the condensed water of forward steam conduit into return water conduit
NL192963C (nl) * 1991-02-15 1998-06-03 Geert Pieter Froma Warmtewisselaar.
KR101265597B1 (ko) * 2006-06-23 2013-05-22 엘지전자 주식회사 복합 의류 처리 시스템
ITBO20080716A1 (it) * 2008-11-28 2010-05-29 Rivacold S R L Dispositivo per la condensazione di vapore e per il recupero energetico
US9557081B2 (en) * 2011-02-25 2017-01-31 Petroliam Nasional Berhad (Petronas) Apparatus for cooling hot condensate in a piping
CN110197321B (zh) * 2019-04-17 2021-06-22 无锡利信能源科技有限公司 一种基于多机组供热单元协同供热安全经济调度的方法

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Publication number Publication date
ATE31218T1 (de) 1987-12-15
US4550687A (en) 1985-11-05
WO1983002658A1 (fr) 1983-08-04
AU1151183A (en) 1983-08-12
PT76131B (de) 1985-12-05
ES8400185A1 (es) 1983-10-16
DE3374807D1 (en) 1988-01-14
KR840003346A (ko) 1984-08-20
PT76131A (de) 1983-02-01
ES519175A0 (es) 1983-10-16
JPS59500064A (ja) 1984-01-12
EP0084846A1 (fr) 1983-08-03

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