EP0518880A1 - Vorrichtung zur indirekten beheizung von fluiden. - Google Patents
Vorrichtung zur indirekten beheizung von fluiden.Info
- Publication number
- EP0518880A1 EP0518880A1 EP91904137A EP91904137A EP0518880A1 EP 0518880 A1 EP0518880 A1 EP 0518880A1 EP 91904137 A EP91904137 A EP 91904137A EP 91904137 A EP91904137 A EP 91904137A EP 0518880 A1 EP0518880 A1 EP 0518880A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat
- coil
- pipe
- longitudinal ribs
- radiators
- 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
Links
- 238000010438 heat treatment Methods 0.000 title claims abstract description 30
- 239000012530 fluid Substances 0.000 title claims abstract description 25
- 238000000034 method Methods 0.000 claims abstract description 6
- 230000008569 process Effects 0.000 claims abstract description 6
- 230000005855 radiation Effects 0.000 claims description 64
- 239000000446 fuel Substances 0.000 claims description 14
- 239000007789 gas Substances 0.000 claims description 11
- 239000000919 ceramic Substances 0.000 claims description 9
- 239000000463 material Substances 0.000 claims description 6
- QVGXLLKOCUKJST-UHFFFAOYSA-N atomic oxygen Chemical compound [O] QVGXLLKOCUKJST-UHFFFAOYSA-N 0.000 claims description 5
- 239000000835 fiber Substances 0.000 claims description 5
- 239000000203 mixture Substances 0.000 claims description 5
- 239000001301 oxygen Substances 0.000 claims description 5
- 229910052760 oxygen Inorganic materials 0.000 claims description 5
- 238000004804 winding Methods 0.000 claims description 2
- 230000001105 regulatory effect Effects 0.000 claims 1
- QTBSBXVTEAMEQO-UHFFFAOYSA-N Acetic acid Chemical compound CC(O)=O QTBSBXVTEAMEQO-UHFFFAOYSA-N 0.000 description 15
- 238000013461 design Methods 0.000 description 9
- 238000002485 combustion reaction Methods 0.000 description 8
- 238000012546 transfer Methods 0.000 description 7
- MWUXSHHQAYIFBG-UHFFFAOYSA-N nitrogen oxide Inorganic materials O=[N] MWUXSHHQAYIFBG-UHFFFAOYSA-N 0.000 description 6
- 239000000567 combustion gas Substances 0.000 description 5
- 239000003546 flue gas Substances 0.000 description 5
- UGFAIRIUMAVXCW-UHFFFAOYSA-N Carbon monoxide Chemical compound [O+]#[C-] UGFAIRIUMAVXCW-UHFFFAOYSA-N 0.000 description 4
- 239000007788 liquid Substances 0.000 description 4
- 238000010276 construction Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 238000013021 overheating Methods 0.000 description 3
- 238000000197 pyrolysis Methods 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 239000010779 crude oil Substances 0.000 description 2
- 238000004821 distillation Methods 0.000 description 2
- 230000008020 evaporation Effects 0.000 description 2
- 229930195733 hydrocarbon Natural products 0.000 description 2
- 150000002430 hydrocarbons Chemical class 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000000630 rising effect Effects 0.000 description 2
- 239000004215 Carbon black (E152) Substances 0.000 description 1
- 238000010521 absorption reaction Methods 0.000 description 1
- 150000001298 alcohols Chemical class 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 229910002091 carbon monoxide Inorganic materials 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 239000000571 coke Substances 0.000 description 1
- 238000004939 coking Methods 0.000 description 1
- 230000006378 damage Effects 0.000 description 1
- 238000000354 decomposition reaction Methods 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 239000004744 fabric Substances 0.000 description 1
- 239000002657 fibrous material Substances 0.000 description 1
- 230000017525 heat dissipation Effects 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 239000003350 kerosene Substances 0.000 description 1
- 150000002561 ketenes Chemical class 0.000 description 1
- 239000011159 matrix material Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 239000003348 petrochemical agent Substances 0.000 description 1
- 239000003208 petroleum Substances 0.000 description 1
- 239000011148 porous material Substances 0.000 description 1
- 238000012545 processing Methods 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 238000007493 shaping process Methods 0.000 description 1
- 239000000126 substance Substances 0.000 description 1
- 230000003685 thermal hair damage Effects 0.000 description 1
- 230000008646 thermal stress Effects 0.000 description 1
- 230000001960 triggered effect Effects 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
- F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
- F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
- F24H1/40—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water tube or tubes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
- F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F21/00—Constructions of heat-exchange apparatus characterised by the selection of particular materials
- F28F21/04—Constructions of heat-exchange apparatus characterised by the selection of particular materials of ceramic; of concrete; of natural stone
- F28F21/045—Constructions of heat-exchange apparatus characterised by the selection of particular materials of ceramic; of concrete; of natural stone for domestic or space-heating systems
Definitions
- the invention relates to a device for the indirect heating of fluids according to the preamble of patent claim 1.
- Devices of this type are required, in particular, for carrying out high-temperature processes, such as are frequently encountered in petroleum processing and in petrochemicals.
- the fluid to be heated is required, in particular, for carrying out high-temperature processes, such as are frequently encountered in petroleum processing and in petrochemicals.
- liquid or gaseous hydrocarbons or a hydrocarbon / steam mixture is usually in
- Heat exchanger tubes are led through a boiler room and heated through the tube wall of the heat exchanger tubes without coming into direct contact with the heating medium.
- the heat transfer to the pipe wall mostly takes place mainly through heat radiation, which emanates from a free flame of a fuel burned in the boiler room, and to a lesser extent through the hot combustion gases in the way of
- the heat exchanger tubes run through the boiler room in the form of coils.
- the major disadvantage of open flames is that a desired geometric shape of the flame and a temperature distribution that is as uniform as possible can only be set with great difficulty. Even under changing operating conditions, uniform heating conditions can hardly be achieved.
- the limits for corresponding control interventions are set very narrowly, changes in the flame geometry are synonymous with changes in the spacing of individual points of the heat exchanger tubes from the "flame surface". This means that the heat flow through the heat exchanger tubes always shows considerable fluctuations not only along the coil. An uneven heat flow is particularly noticeable over the circumference of the heat exchanger tubes, since the individual pieces of the
- Liquid fuels can be burned practically without flame formation in a burner with a heat radiation surface by passing the gaseous fuel mixed with an oxygen-containing gas (e.g. air) through a porous radiation body and igniting and burning it on the river surface. The ignition takes place through the glow of this outer surface (heat radiation surface).
- an oxygen-containing gas e.g. air
- Fuel supply does not change.
- the temperature distribution within the heat radiation area is very even.
- Such a burner with a heat radiation surface is known, for example, from US Pat. No. 4,722,681.
- a radiation body is formed from a ceramic fiber matrix and has a large length and width in comparison to the structural depth of the burner, so that there is a large heat radiation area. This burner is intended for the heat treatment of long webs of paper or fabric.
- a flat coil is passed as a heat exchanger.
- the fluid to be treated flows in the coil and is indirectly heated as a result of the heat radiation.
- the radiant heater which as
- Fiber burner is formed and arranged on the floor of the boiler room, releases hot combustion gases by combustion, which
- Pipe coil of the heat exchanger lies in a vertical plane, the pipes of the individual turns of the pipe coil being arranged essentially horizontally.
- a heating apparatus is known from EP 0 385 963 A1, which is formed from a cylindrical housing in which a likewise
- cylindrical ceramic hollow body is arranged with a porous wall.
- a cylindrical heat exchanger is also built into the housing, through which a heat transfer medium flows.
- a mixture of a gaseous substance under excess pressure can be
- Fuel and an oxygen-containing gas are introduced, which flows through the ceramic body and burns after ignition on the inner surface of the ceramic body.
- the hot flue gases generated by the combustion can pass through suitable openings in the
- This heater in which a large part of the heat absorbed by the heat exchanger is transferred by convection, is primarily intended as a boiler for heating buildings and is not suitable for carrying out high-temperature processes.
- the fluid to be heated is introduced into the heat exchanger from above and drawn off again at the bottom, so that the "transport direction" of the
- Pipe coil is opposed to the upward flow of combustion gases.
- Vaporized liquid fuels such as kerosene, diesel, naphtha or alcohols are intended for combustion.
- Heat exchanger tube coil is exposed to strong heat radiation, while the upper parts can no longer be reached by the heat radiation from the burner and are essentially heated by convection. But even the lowest heat exchanger tube can
- Heat exchanger tube the tops of the heat exchanger tubes are not directly irradiated at all. This means that the heat flow is subject to considerable fluctuations both in the circumferential direction of the heat exchanger tubes and in the transport direction of the heat exchanger.
- the object of the invention is to propose a generic device for the indirect heating of fluids, in which a much more uniform heat flow in the heat exchanger is guaranteed.
- the invention provides that the tubes of the heat exchanger coils through which the fluid to be heated is passed are each irradiated by two heat radiators which are located on opposite sides with respect to the tube axis and with respect to the area into which the coil extends. Each coil is therefore arranged between two heat radiators directed towards one another with their heat radiation, so that there are no longer any unexposed surfaces facing away from the tube circumference. Since the heat radiation areas of the heat radiators each have a shape corresponding to the areal extent of the heat exchanger tube coil, the direction of travel can also be reduced
- the heat exchanger coils generally do not represent a closed area, but that there is a free space between the individual turns. This means that the heat radiation from the two opposite heat radiators pass through these gaps and become undesirable
- the invention therefore provides for two diametrically opposed longitudinal ribs to be arranged on the outside of the heat exchanger tubes, which extend over the entire or almost entire length of the tubes and each protrude into the spaces between the coils. These longitudinal ribs thus represent an obstacle to the passage of the
- Longitudinal fins can absorb significant amounts of heat due to the heat radiation, the heat flow can be intensified through the areas of the tube walls lying laterally to the direction of radiation of the heat radiators, i.e. through the less strongly irradiated tube wall areas, by additional heat flowing from these longitudinal fins into these lateral areas by heat conduction.
- the longitudinal ribs should therefore have the best possible contact with the pipe surface (eg welded connection). It can also be expedient to use a material with a higher thermal conductivity than the tube material for the longitudinal ribs. Since the heat flow depends directly on the cross-sectional area in the direction of flow, the thickness of the longitudinal ribs should be designed so that the heat input from the longitudinal ribs reduces the heat input into the lateral areas of the pipes as a result of the
- the minimum thickness of the longitudinal ribs required for this can be determined by calculation in a known manner. In some cases, it may be appropriate to use longitudinal ribs that have an approximately trapezoidal shape instead of longitudinal ribs of constant thickness
- the coil of the heat exchanger through which the fluid is guided, expediently has a flat extension, i.e. the coils of the pipe coil lie in one plane. Basically, the
- Radiant body can be adapted to this area.
- a cylindrical surface is recommended in such a case, the heat exchanger tubes being able to be arranged, for example, in a helical shape.
- the term “pipe coil” is also intended to include this embodiment.
- the tubes can also run parallel to the cylinder jacket lines, for example.
- each coil surface is assigned two heat radiators located opposite one another. It is possible to place the heat radiators located between two adjacent coils in a single burner housing with two heat radiation surfaces radiating in the opposite direction
- Heat radiation surfaces add up to a total heat radiation surface corresponding to the surface of the heat exchanger.
- the conventional design does not allow such specifically different heating, since the combustion gases rising upwards from the burners arranged below in the boiler room inevitably influence the effect of the burners arranged above.
- the invention allows the temperature gradient of the fluid on its way through the
- Heat radiators can be carried out (e.g. electrically heated
- burners with porous radiation bodies are particularly suitable, on the glowing surface of which gaseous fuels can be burned flameless with oxygen-containing gas. Be particularly preferred
- Ceramic fiber burner This type of heat radiation source is not only characterized by simple handling, low pressure drops, quick response to load fluctuations and low noise levels, but also by extremely low levels of nitrogen oxides (less than 20 ppm), carbon monoxide and unburned fuel in the combustion exhaust gas. The ability to adjust the geometry of the
- Heat radiators with a vertically arranged heat radiation surface are preferred.
- the invention can also be carried out with horizontal heat radiation surfaces.
- Figure 1 shows a schematic cross section through a
- FIG. 2a shows a cross or longitudinal section through a conventional and 2b furnace for the pyrolysis of acetic acid
- Figure 3a shows a cross or longitudinal section through a
- FIG. 4 shows a cross section through a heat exchanger tube with trapezoidal longitudinal ribs
- Figure 5 shows a cross section through a turn of a
- Figure 6 shows a part of a cross section through an inventive
- Figure 7 shows a section through a conventional oven for the
- Figure 1 shows a cross section in a vertical plane of a
- Pipe coils 4 each have diametrically opposite and vertically outwardly projecting longitudinal ribs 5 on their top and bottom sides, which are welded to the outside of the pipe.
- the heat radiators 1 have a radiation body 15 made of a porous material (e.g. ceramic fiber material), which is embedded in a burner housing, which is open to the side facing the pipe coil 4. Through a gas inlet 2, a mixture of a
- Pipe sections of the coil 4 with their outer end faces are close together or even meet, the space between the tubes of the coil 4 is practically completely shielded against direct passage of heat radiation from one heat radiator 1 to the other heat radiator 1, so that these are not mutually exclusive can negatively influence.
- the heat absorbed by the longitudinal ribs 5 is in each case introduced into the wall of the tubes of the tube coil 4 by heat conduction and from there passed on to the fluid passed through.
- the thickness of the longitudinal ribs 5 is designed, taking into account their thermal conductivity, such that the heat flow that can be passed through them is sufficient to cover the area in the upper and lower surface areas (in the area of the 12 o'clock and 6 o'clock positions) reduced heat radiation (in comparison to the 3 o'clock and 9 o'clock positions) approximately compensate for the lower heat absorption or at least significantly reduce the differences.
- FIGS. 2a and 2b a reaction furnace, for example for the pyrolysis of acetic acid for the production of ketenes, is shown in FIGS. 2a and 2b.
- the heating chamber 14 is surrounded by a heat-insulated housing 7.
- the coils, designated 6, of the two heat exchangers arranged in parallel vertical planes, through which the acetic acid is passed, are mounted on a hanging device 10 in the heating chamber 14.
- the lowermost heat exchanger tubes of the coils 6 are connected to the feed lines 8 and the top ones
- Heat exchanger tubes connected to the discharge lines 9, so that the direction of transport of the acetic acid through the heat exchanger is in principle directed from bottom to top, although the coils 6 in
- burners 11 run essentially horizontally.
- Heat exchangers can be operated overall with higher efficiency. This means that either with the same heat exchange surface of a coil, a larger amount of heat or with the same maximum permissible
- Heat exchange surface can be transferred.
- Heat transfer performance is always an average between the maximum heat flow in the areas most exposed to heat radiation and the minimum heat flow in the areas of the heat exchanger tubes least exposed to heat radiation.
- the ratio of the average to the maximum heat flow in conventional heat exchangers is approximately 1: 1.2.
- the design according to the invention makes it possible to bring this ratio to almost 1: 1, since the entire surface of the heat exchanger tubes is almost the same height
- the maximum permissible pipe wall temperature does not only depend on the temperature resistance of the pipe material, but is also very significantly determined by the thermal properties of the heated fluid. For example, decomposition reactions can take place above certain critical temperatures (e.g.
- the invention enables an operating mode in which even exceeding the critical temperature limit, which is strictly local, can be reliably avoided, without at the same time
- the temperature level of the heat exchanger on average would have to be reduced significantly below this critical limit.
- FIGS. 3a and 3b show a furnace according to the present invention corresponding to the furnace from FIGS. 2a and 2b in a vertical longitudinal or cross-section.
- the housing 7th In the through the housing 7th
- enclosed boiler room 14 are four coils 4 as
- Heat exchanger tubes in vertical planes parallel to each other
- Pipe coils 4 take place through a common line (feed collector 13).
- a discharge collector (not shown) is provided for the discharge line 9 of the heated fluid.
- the heat exchanger tubes of the tube coil 4 attached to the hanging devices 10 on the housing 7 do not run essentially horizontally but vertically within the vertical plane (in the parallel tube sections). The general direction of transport of the fluid through the
- the heat exchanger is therefore horizontal. Everyone on both flat sides
- Pipe coil 4 is arranged in parallel at a distance from a heat radiator 1, the heat radiation surfaces 3 of which correspond in their extension to the areal extent of the pipe coil 4.
- the gas inlet 2 for supplying the heat radiators 1 designed as a fiber burner is designed as a common manifold. The resulting are called
- Combustion gases are led out of the heating chamber 14 through the flue gas opening 12. Except for those on the outside
- the other heat radiators 1 are each provided with 2 heat radiation surfaces 3 acting in the opposite direction, i.e. they act like two separate heat radiators 1.
- the longitudinal ribs 5 attached to the heat exchanger tubes of the tube coils 4 close by a complete shielding of the an undesirable mutual influence of the heat radiators 1 directed against each other in their radiation direction between the individual opposing pipe strands.
- the longitudinal ribs 5 ensure the already described increase in the heat flow in the areas of the heat exchanger tube walls which are less affected by the direct heat radiation.
- the heat radiation surfaces 3 may be brought relatively close to the coils 4. This enables an exceptionally compact design of the device.
- a similar approach of the burners with a free flame would inevitably lead to local overheating on the heat exchanger tubes. Therefore, a conventional oven has a much larger one with the same heat transfer performance
- Boiler room volume For the embodiment according to the invention, this results in a reduction in the required space to only a third of the previous value, as can be seen approximately from a comparison of FIGS. 2b and 3b.
- the smaller volume means that the radiation losses to the outside are correspondingly lower. This leads together with the increase in
- FIG. 4 shows a single heat exchanger tube of a tube coil 4, the longitudinal ribs 5a of which are approximately trapezoidal in cross section, the cross section widening towards the tube surface.
- This shape takes into account the fact that the heat dissipation only has to take place in the direction of the heat exchanger tube and the amount of heat to be dissipated to the tube surface increases steadily over the height of the longitudinal fin.
- the thickness of the longitudinal ribs is thus designed depending on the distance to the pipe surface in such a way that the cross-section which is at least required for the respective amount of heat is ensured. Compared to a design based on the maximum required cross section (constant over the entire height of the longitudinal ribs), this type of design leads to material and weight savings without the
- FIG. 5 directly abut each other and align with one another, a modification is shown in FIG. 5 in which the longitudinal ribs 5b overlap one another in their vertical extent (from the tube surface). This has the advantage that a complete shielding of the spaces between the strands of the coil 4 can always be guaranteed. This would also be possible by using a single one instead of two longitudinal ribs
- FIG. 6 shows a detail of an embodiment of the invention, in which the tube coil 4 and the heat radiation surfaces 3 of the radiation bodies 15 of the heat radiators 1 have a curved shape, namely a cylindrical jacket shape.
- the pipe coil 4 is in the form of parallel rings or in the form of a helix
- the fuel consumption of the furnace according to the invention is 37% lower and the output is on
- Nitrogen oxides are more than 80% lower than with a conventional furnace.
- there is the considerably more compact design which is documented in the fact that the coil area is around 30% smaller, the volume of the boiler room is 66% smaller and the surface of the boiler room is 54% smaller.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- General Engineering & Computer Science (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- Geometry (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Ceramic Engineering (AREA)
- Thermotherapy And Cooling Therapy Devices (AREA)
- General Induction Heating (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Resistance Heating (AREA)
- Gas Burners (AREA)
- Catching Or Destruction (AREA)
- Central Heating Systems (AREA)
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT47720A IT1240789B (it) | 1990-03-05 | 1990-03-05 | Apparato per processi termici ad alta temperatura, con sorgente di calore ad incandescenza a superfici radianti e serpentini per il fluido di processo. |
IT4772990 | 1990-03-05 | ||
PCT/DE1991/000183 WO1991014139A1 (de) | 1990-03-05 | 1991-02-27 | Vorrichtung zur indirekten beheizung von fluiden |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0518880A1 true EP0518880A1 (de) | 1992-12-23 |
EP0518880B1 EP0518880B1 (de) | 1994-09-21 |
Family
ID=11262092
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP91904137A Expired - Lifetime EP0518880B1 (de) | 1990-03-05 | 1991-02-27 | Vorrichtung zur indirekten beheizung von fluiden |
Country Status (11)
Country | Link |
---|---|
US (1) | US5320071A (de) |
EP (1) | EP0518880B1 (de) |
JP (1) | JPH05506709A (de) |
AT (1) | ATE112040T1 (de) |
CA (1) | CA2077675A1 (de) |
DE (1) | DE59103050D1 (de) |
DK (1) | DK0518880T3 (de) |
ES (1) | ES2060367T3 (de) |
IT (1) | IT1240789B (de) |
NO (1) | NO177653C (de) |
WO (1) | WO1991014139A1 (de) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US5799724A (en) * | 1997-07-22 | 1998-09-01 | The Babcock & Wilcox Company | Trapezoidal deflectors for heat exchanger tubes |
US7440852B2 (en) * | 2003-03-31 | 2008-10-21 | Council Of Scientific And Industrial Research | Stochastic analytical solution to quantify the earth's subsurface heat flow |
US6668762B1 (en) | 2003-04-17 | 2003-12-30 | Parviz Khosrowyar | Indirect fired process heater |
US7856949B2 (en) * | 2007-12-18 | 2010-12-28 | Ppg Industries Ohio, Inc. | Heat pipes and use of heat pipes in furnace exhaust |
EP2318759B1 (de) * | 2008-06-12 | 2018-10-31 | Processi Innovativi Srl | Verbrennungssystem zur hochtemperatur-wärmeübertragung |
RU2684293C1 (ru) * | 2016-07-01 | 2019-04-05 | Государственное бюджетное образовательное учреждение высшего образования Нижегородский государственный инженерно-экономический университет (НГИЭУ) | Устройство для нагрева воды |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2578136A (en) * | 1946-05-24 | 1951-12-11 | Huet Andre | Tangentially finned heat exchange tubes |
CH305379A (fr) * | 1952-03-28 | 1955-02-28 | Thermo Mecanique Soc | Appareil thermique. |
US3003481A (en) * | 1960-06-17 | 1961-10-10 | Yuba Cons Ind Inc | Double fired vertical tube heater |
GB949758A (en) * | 1962-11-28 | 1964-02-19 | Universal Oil Prod Co | Fluid heater |
SU1250825A1 (ru) * | 1985-02-21 | 1986-08-15 | Предприятие П/Я Р-6193 | Теплообменна поверхность |
WO1986006155A1 (en) * | 1985-04-08 | 1986-10-23 | Miura Co., Ltd. | Surface combustion type fluid heater |
IT206653Z2 (it) * | 1985-12-23 | 1987-10-01 | Ferroli Paolo | Elemento di caldaia ad alette scambiatrici a sezione trasversale ovale o ad ala d'aereo. |
US4658762A (en) * | 1986-02-10 | 1987-04-21 | Gas Research Institute | Advanced heater |
-
1990
- 1990-03-05 IT IT47720A patent/IT1240789B/it active IP Right Grant
-
1991
- 1991-02-27 WO PCT/DE1991/000183 patent/WO1991014139A1/de active IP Right Grant
- 1991-02-27 EP EP91904137A patent/EP0518880B1/de not_active Expired - Lifetime
- 1991-02-27 JP JP91504189A patent/JPH05506709A/ja active Pending
- 1991-02-27 CA CA002077675A patent/CA2077675A1/en not_active Abandoned
- 1991-02-27 US US07/934,677 patent/US5320071A/en not_active Expired - Fee Related
- 1991-02-27 ES ES91904137T patent/ES2060367T3/es not_active Expired - Lifetime
- 1991-02-27 DK DK91904137.6T patent/DK0518880T3/da active
- 1991-02-27 DE DE59103050T patent/DE59103050D1/de not_active Expired - Fee Related
- 1991-02-27 AT AT91904137T patent/ATE112040T1/de not_active IP Right Cessation
-
1992
- 1992-09-03 NO NO923440A patent/NO177653C/no unknown
Non-Patent Citations (1)
Title |
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See references of WO9114139A1 * |
Also Published As
Publication number | Publication date |
---|---|
CA2077675A1 (en) | 1991-09-06 |
NO923440L (no) | 1992-09-03 |
IT1240789B (it) | 1993-12-17 |
IT9047720A0 (it) | 1990-03-05 |
DK0518880T3 (da) | 1994-10-17 |
ES2060367T3 (es) | 1994-11-16 |
IT9047720A1 (it) | 1991-09-05 |
EP0518880B1 (de) | 1994-09-21 |
DE59103050D1 (de) | 1994-10-27 |
NO177653B (no) | 1995-07-17 |
WO1991014139A1 (de) | 1991-09-19 |
JPH05506709A (ja) | 1993-09-30 |
NO177653C (no) | 1995-10-25 |
NO923440D0 (no) | 1992-09-03 |
US5320071A (en) | 1994-06-14 |
ATE112040T1 (de) | 1994-10-15 |
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