EP0084846A1 - 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

Info

Publication number
EP0084846A1
EP0084846A1 EP83100408A EP83100408A EP0084846A1 EP 0084846 A1 EP0084846 A1 EP 0084846A1 EP 83100408 A EP83100408 A EP 83100408A EP 83100408 A EP83100408 A EP 83100408A EP 0084846 A1 EP0084846 A1 EP 0084846A1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
feed water
condensate
exchanger according
container
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
EP83100408A
Other languages
German (de)
English (en)
Other versions
EP0084846B1 (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

Links

Images

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 method for operating a high-pressure steam boiler, in particular for dry cleaning, laundry or the like, with consumers connected to a high-pressure steam boiler, the condensate of which is returned to a condensate container, from which the steam boiler is fed by means of a feed water pump Feed water is supplied and the condensate and feed water are fed to a heat exchanger upstream of the condensate tank.
  • the invention further relates to a device (heat exchanger) which is particularly suitable and intended for carrying out the method.
  • 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 water 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 in the boiler, either the condensate container is made very large or the condensate is additionally cooled. On the other hand, this leads to difficulties again if the condensate is too cold (eg 60 ° C), because then the boiler heating surfaces or pipes will rot.
  • the invention is therefore based on the object to improve the operating conditions of such a steam boiler system in such a way that the heat content of the condensate is used, the heating-up time of the boiler is shortened and no damage to the lines and the boiler, for example due to the failure of SO 2 .
  • This object is achieved according to the invention essentially in that the hot condensate is fed to the free space of the heat exchanger, the feed water to be heated is pumped to the heat exchanger, guided in a spiral from the cold to the warm area in the heat exchanger and passed from the heat exchanger into the steam boiler.
  • the process is advantageously carried out in such a way that the condensate flowing in at a temperature of approx. 90-105 ° C. cools down to approx. 50 ° C. in the heat exchanger and again from the feed water tank at a temperature of approx. 40 ° C. to the heat exchanger fed and fed to the steam boiler at a temperature of about 90-95 ° C, or higher.
  • the invention is also based on the object to provide a device, in particular a heat exchanger, with which the heat of the condensate is reduced
  • a device in particular a heat exchanger, with which the heat of the condensate is reduced
  • Steam boiler system for increasing the temperature of the feed water can be optimally used, the highest possible energy savings can be achieved for the operation of the steam boiler and can be easily adapted to different operating conditions or different sizes of the high-pressure steam boiler, for example higher output, and further the performance of the heat exchanger can be controlled depending on the amount of condensate.
  • a heat exchanger which is particularly suitable for carrying out the method according to the invention and which consists of a container with a pipe arranged therein for the one medium and connection for the second medium, in that in the lid of the container Mouth connections for a first condensate line, a feed water supply line and a feed water discharge line, and a second condensate line are provided that a feed water spiral is arranged between the feed water supply line and the feed water discharge line and extends over the height of the container , wherein the feed water supply line extends to the lowest point of the feed water spiral and the feed water discharge line extends from the highest point of the feed water spiral.
  • 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 of about 60 ° C in the feed water spiral is heated to approx. 90-95 ° C and also higher by the fresh condensate before the boiler enters.
  • the condensate line is connected to consumers and leads to a feed water tank, 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 designed as a flat spiral at its upper end.
  • the flat spiral can, according to a first embodiment, be flat or, according to modifications, upward to concave or convex.
  • an, for example, conical baffle plate force jet plate
  • a conical baffle plate extending from the lid and reaching to the level of the flat spiral
  • the vapor is guided to the place of the feed water spiral, which is located at the heat exchanger inlet.
  • the temperature of the boiler feed water is increased again by approx. 5 ° C.
  • a recirculation plate is provided below the flat spiral according to a development of the invention.
  • This design has the essential advantage that the hot fresh condensate in the area the flat spiral develops an intense turbulence and releases a larger 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 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 take place 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 that can be connected to the tank and is provided with the closable pipe section is provided with connections for the condensate line, a first feed water line and a second feed water line, with a feed water flat spiral, a baffle plate and a recirculation plate and with connecting means between the feed water lines and the feed water flat spiral of the pipe section Feed water pipe of the flat spiral of the tank.
  • 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 recirculation plate in the pipe section can be designed analogously to the recirculation plate in the heat exchanger tank itself.
  • the recirculation plate is advantageously arranged on the feed water supply line of the pipe section.
  • the recirculation plate is flat.
  • the recirculation plate In order to conduct the vapor vapor back up through the recirculation plate, the recirculation plate is advantageously concave towards the cover.
  • the recirculation plate can be profiled.
  • the diameter of the recirculation plate is smaller. than the inside diameter of the pipe weft.
  • the diameter of the recirculation plate is larger than the free inner diameter of the baffle plate.
  • the recirculation plate can also be arranged in a height-adjustable manner in the pipe section in order to adapt to the throughput of the vapor.
  • Drive means for height adjustment means (des) of the recirculation plates (s) are advantageously provided hen.
  • 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 condensate line is designed as a riser line to the condensate container arranged at a higher level than the location of the heat exchanger.
  • the configuration according to the invention ensures that a dynamic pressure which ensures the function of the heat exchanger is created. Since the heat exchanger in the pressure range of + 0.2 bar works, the non-return valve prevents the thermally used condensate from being 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 with the container is thermally insulated.
  • a high-pressure steam boiler system is shown schematically, with which the inventive method is carried out.
  • 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 dry cleaning or in a laundry, ironing machines, steaming dolls, steaming 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) tank 5, in which the The condensate cools down. 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 before it enters the condensate container 5.
  • the heat of the condensate flowing back at a temperature of about 90-105 ° C. is given off to the feed water, so that the condensate has a temperature of about 50 ° C. when it leaves the heat exchanger 8 and at this temperature into the feed water tank 5 entry. Due to the cooling in the container 5, the temperature of the feed water after the pump 7 drops to about 40 ° C. Through the heat exchange in the heat exchanger 8, the temperature of the boiler water is then increased again to approximately 80-105 ° C.
  • a heat exchanger 8 according to the invention is shown in longitudinal section.
  • 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.
  • an additional flat spiral starting from the cover 1 7 , it is appropriate Baffle plate 16 (forced beam plate) provided.
  • 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.
  • boiler 1 By increasing the temperature of the boiler feed water to approx. 80 - 105 ° C, on the one hand it is achieved that boiler 1 can start its full operation in approx. 15 - 30 minutes and that the sulfur content in the heating oil for the boiler always remains gaseous, So that no S0 2 fails and sooting of the heating surfaces of the boiler 1 is avoided.
  • a recirculation plate 18 is provided below this flat spiral 12.
  • This, preferably round, recirculation plate 18 is expediently 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 be.
  • 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.
  • 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.
  • FIG. 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 windings 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 ".
  • feedwater spiral 11 or the approximately flat feedwater 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 dwell 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 to be height-adjustable. 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 take place which control the drive means 26 as a function of 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 a cross-section according to lines II and II-II of FIG. 7 in the planes of the flat spirals 12 ', 12 "the assignment of the individual lines and spirals as well as the baffle plates 16', 16" and the 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 height difference 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 division of the heat rope shear in two zones enables the condensate that occurs to suddenly relax, ie expand and expand to a gas volume in the sense of the state of the aggregate 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 with 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.
  • the invention is not restricted to the exemplary embodiments shown and described. It also includes all professional modifications and further training as well as partial and sub-combinations of the features and measures shown or described.

Landscapes

  • 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)
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
DE3224153 1982-06-29
DE19823224153 DE3224153A1 (de) 1982-06-29 1982-06-29 Waermetauscher zum betrieb eines hochdruck-dampfkessels
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 true EP0084846A1 (fr) 1983-08-03
EP0084846B1 EP0084846B1 (fr) 1987-12-02

Family

ID=27432771

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83100408A Expired EP0084846B1 (fr) 1982-01-23 1983-01-19 Exchangeur de chaleur pour une installation comportant une chaudière à vapeur surchauffée

Country Status (10)

Country Link
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) ES8400185A1 (fr)
PT (1) PT76131B (fr)
WO (1) WO1983002658A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL9100270A (nl) * 1991-02-15 1992-09-01 Geert Pieter Froma Warmtewisselaar met een spiraalvormig omlopend kanaal alsmede ketel met een dergelijke warmtewisselaar.
CN110197321A (zh) * 2019-04-17 2019-09-03 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

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE157408C (fr) *
FR359272A (fr) * 1905-11-09 1906-03-20 Marie Edmond Philbert Chaboche Perfectionnements aux chaudières à vaporisation instantanée en vue de l'utilisation des chaleurs perdues
GB190913325A (en) * 1908-08-03 1909-12-23 Eduard Nager An Improvement in Steam Heating Installations.
US1939415A (en) * 1931-05-04 1933-12-12 Fred H Schaub Heat exchange system
FR809263A (fr) * 1935-08-08 1937-02-27 Klein Dispositif de retour de l'eau de condensation chaude dans la pompe d'alimentation principale des chaudières à vapeur
US2581146A (en) * 1948-09-09 1952-01-01 Fred H Schaub Engineering Co I Boiler feedwater system
US3799256A (en) * 1971-11-18 1974-03-26 P Gaines Apparatus for transferring heat

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1938072A (en) * 1932-05-10 1933-12-05 Dunlop Tire & Rubber Corp Method and apparatus to control the concentration of boiler waters
US2115548A (en) * 1935-04-27 1938-04-26 Foster Wheeler Corp Heating
US3367309A (en) * 1966-05-10 1968-02-06 Erwin L. Plagman Jr. High-pressure dry steam system and method of controlling the same
US4202406A (en) * 1978-06-29 1980-05-13 Avery Alfred J Heat exchange system

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE157408C (fr) *
FR359272A (fr) * 1905-11-09 1906-03-20 Marie Edmond Philbert Chaboche Perfectionnements aux chaudières à vaporisation instantanée en vue de l'utilisation des chaleurs perdues
GB190913325A (en) * 1908-08-03 1909-12-23 Eduard Nager An Improvement in Steam Heating Installations.
US1939415A (en) * 1931-05-04 1933-12-12 Fred H Schaub Heat exchange system
FR809263A (fr) * 1935-08-08 1937-02-27 Klein Dispositif de retour de l'eau de condensation chaude dans la pompe d'alimentation principale des chaudières à vapeur
US2581146A (en) * 1948-09-09 1952-01-01 Fred H Schaub Engineering Co I Boiler feedwater system
US3799256A (en) * 1971-11-18 1974-03-26 P Gaines Apparatus for transferring heat

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
POWER, Band 93, März 1949, Seiten 114-117 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
NL9100270A (nl) * 1991-02-15 1992-09-01 Geert Pieter Froma Warmtewisselaar met een spiraalvormig omlopend kanaal alsmede ketel met een dergelijke warmtewisselaar.
CN110197321A (zh) * 2019-04-17 2019-09-03 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

Also Published As

Publication number Publication date
JPS59500064A (ja) 1984-01-12
EP0084846B1 (fr) 1987-12-02
ES519175A0 (es) 1983-10-16
ATE31218T1 (de) 1987-12-15
PT76131A (de) 1983-02-01
PT76131B (de) 1985-12-05
US4550687A (en) 1985-11-05
DE3374807D1 (en) 1988-01-14
WO1983002658A1 (fr) 1983-08-04
ES8400185A1 (es) 1983-10-16
KR840003346A (ko) 1984-08-20
AU1151183A (en) 1983-08-12

Similar Documents

Publication Publication Date Title
DE3213837C2 (de) Abgasdampferzeuger mit Entgaser, insbesondere für kombinierte Gasturbinen-Dampfkraftanlagen
DE2430208A1 (de) Verfahren zum zwischenueberhitzen von teilentspanntem dampf und atomkraftanlage zum durchfuehren des verfahrens
EP0425717A1 (fr) Générateur de vapeur à passage unique
DE2311066A1 (de) Dampferzeuger fuer ungefeuerte kraftanlage
EP1794495B1 (fr) Generateur de vapeur en continu chauffe a l'aide d'un combustible fossile
EP0410111B1 (fr) Chaudière de récupération de chaleur pour une centrale à turbine à gaz et à vapeur
DE4408284A1 (de) Verbesserte Temperatursteuerung von Dampf für Kessel
EP0084846B1 (fr) Exchangeur de chaleur pour une installation comportant une chaudière à vapeur surchauffée
DE6601963U (de) Kondensatoranordnung bei dampfturbinen
DE647193C (de) Roehrendampferzeuger
DE2115257A1 (de) Wassererhitzer
DD206815A5 (de) Verfahren und vorrichtung zum betrieb eines hochdruck-dampfkessels
DE889597C (de) Dampferzeuger mit mittelbarer Beheizung des Arbeitsmittels
DE1278085B (de) Heinz- und/oder Kuehlgeraet
EP1270877B1 (fr) Transformation de chaleur avec représsurisation
DE801777C (de) Dampftemperaturregler
DE809686C (de) Verfahren zum Beseitigen von in Gaserzeugungsanlagen anfallendem schaedlichem Gaswasser durch Verdampfen desselben mittels des im Dampfmantel eines Gaserzeugers erzeugten Wasserdampfes und Ein-fuehren des Gaswasserdampfes in den Gaserzeuger
DE3224153A1 (de) Waermetauscher zum betrieb eines hochdruck-dampfkessels
EP3472515B1 (fr) Générateur de vapeur vertical à récupération de chaleur
DE2515623A1 (de) Dampferzeuger mit u-foermig gekruemmten rohren
DE102011052430B4 (de) Dampfnutzungsanlage
AT146106B (de) Dampferzeuger mit einem im Feuerraum liegenden Kühlschirm.
DE1401357C (de) Dampferzeuger
DE441469C (de) Vorrichtung zur Ausnutzung der Waerme des abgelassenen Dampfkesselwassers
DE3202144C2 (de) Wärmetauscher zum Betrieb eines Hochdruck-Dampfkessels

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

17P Request for examination filed

Effective date: 19830810

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: JACOB, KARL AUGUST

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH DE FR GB IT LI LU NL SE

REF Corresponds to:

Ref document number: 31218

Country of ref document: AT

Date of ref document: 19871215

Kind code of ref document: T

REF Corresponds to:

Ref document number: 3374807

Country of ref document: DE

Date of ref document: 19880114

ITF It: translation for a ep patent filed

Owner name: DE DOMINICIS & MAYER S.R.L.

ET Fr: translation filed
GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Effective date: 19890119

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 19890726

Year of fee payment: 7

GBPC Gb: european patent ceased through non-payment of renewal fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Effective date: 19900131

Ref country code: CH

Effective date: 19900131

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

ITTA It: last paid annual fee
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 19911230

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19911231

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 19920108

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 19920115

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: LU

Payment date: 19920130

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: NL

Payment date: 19920131

Year of fee payment: 10

EPTA Lu: last paid annual fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 19930119

Ref country code: AT

Effective date: 19930119

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19930120

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Effective date: 19930131

BERE Be: lapsed

Owner name: JACOB KARL AUGUST

Effective date: 19930131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Effective date: 19930801

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Effective date: 19930930

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

EUG Se: european patent has lapsed

Ref document number: 83100408.0

Effective date: 19930810

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20010124

Year of fee payment: 19

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020801