WO1997021968A2 - Wärmetauscher - Google Patents
Wärmetauscher Download PDFInfo
- Publication number
- WO1997021968A2 WO1997021968A2 PCT/EP1996/005491 EP9605491W WO9721968A2 WO 1997021968 A2 WO1997021968 A2 WO 1997021968A2 EP 9605491 W EP9605491 W EP 9605491W WO 9721968 A2 WO9721968 A2 WO 9721968A2
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- heat
- fluid
- channel
- flow
- supply fluid
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D21/0001—Recuperative heat exchangers
- F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
- F28D21/0005—Recuperative heat exchangers the heat being recuperated from exhaust gases for domestic or space-heating systems
- F28D21/0007—Water heaters
-
- 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
- F24H1/24—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers
- F24H1/26—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body
- F24H1/28—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes
- F24H1/287—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes with the fire tubes arranged in line with the combustion chamber
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
- F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
- F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
Definitions
- the invention relates to an apparatus for heating a heat transfer fluid, in which a warm fluid delivery fluid of a heat exchanger with separate channels for the Warmeannon ⁇ and the heat transfer fluid flows through.
- heat exchangers of the type mentioned are e.g. used in boilers. With such heat exchangers there is basically the problem of optimizing the heat transfer from the heating gases to the water serving as the heat transfer fluid. It should also be noted that the heat exchangers should be as small and compact as possible for economic reasons.
- ⁇ S " DE 36 02 608 A 1 shows a double tube, round in cross-sections, for use for cooling hot hydraulic fluids in engines.
- This round double tube has an all-round running on both round tubes and when viewed in the longitudinal direction a the radial
- the invention has for its object to provide a device C " which has optimal heat transfer properties, which optimally cools down the heat supply fluid even under full load conditions, is compact and can be produced inexpensively.
- the channels are formed by a double tube, that the inner tube form the channel for the heat supply fluid and the jacket space between the inner and outer tubes form the channel for the heat transfer fluid in that the tubes are plate-shaped approximately
- the corresponding edge sides of the inner tube and jacket tube described can in each case be spaced apart or coincide as side walls to form common ones.
- the device according to the invention thus has a heat exchanger
- 2-Tscherplatte which has three channels: the plate-shaped heat supply fluid channel, and the two large-area heat transfer port fluid plate channels. Since the double tube is bent once or several times, all three channels have deflections, preferably by 180 °, so that the three-channel
- 3C structure of the heat exchanger plate is also fully retained in the common deflection area.
- the heat transfer fluid plates change the positions "above the heat supply fluid channel” and “below the 7th half of the heat supply fluid channel” after a 180 ° deflection.
- the two heat transfer fluid plates may be edge-side to one or both sides with each other, so that in these cases not a two-part counter-flow of the heat carrying fluid takes place, but an undivided counter ⁇ "Ström the heat transfer fluid the plate-shaped
- the heat supply fluid channel flows around on three sides or on all sides, and this also in the area of the bends or the 180 "deflection.
- the three possible cross sections of the heat exchanger plate thus point around the plate-shaped heat supply fluid channel
- the mass flow of the heat supply fluid from the mass flow 2_0 d of the heat transport fluid is not only on the top and bottom of two separate transport fluid partial flows but on an undivided mass flow either on three sides, i.e. on the top, bottom and one edge side, or on all sides, i.e. on the top -, underside and both edge sides, in countercurrent flow around 2 £ " , a division of the heat transport fluid flow by a simple branching of the lower inflow pipe is not necessary. In this case, a simple pipe connection is sufficient.
- distribution pipes are preferably placed on the lower branch pipe or the upper branch pipe in such a way that they are welded end-to-end onto the end of one heat transfer fluid plate or the end of the other heat transport fluid plate " ⁇ 5 " which of course each have a flow passage to the pipe branches and on the other hand have holes on their welded-on longitudinal sides as passages to the heat transfer fluid plates.
- the terminal manifolds described herein is just one required. Ermögli ⁇ chen a countercurrent also described above in the terminal region, three-channel Heat exchanger plate.
- the heat supply fluid channel is, even when a combustion chamber or a heating gas chamber is connected upstream of the heat exchanger plate described, from the entry of the combustion or heating chamber at the flange and further via the channel-shaped connection to the plate-shaped ⁇ heating gas channel, the middle layer of the heat exchanger plate described, and in the further course of the plate-shaped heating gas channel up to the outlet nozzle there is always an undivided channel which causes an undivided flow of the heating fluid or heating gas -
- 2.0 ström is always undivided and plate-shaped in the area of the internal delivery fluid channel.
- Heat exchanger plate be common, identical partitions.
- the bend or bends are necessary because the laminar IS " partial flows of the heat supply fluid flow, which cause a heat stratification, due to the turbulence that arises ⁇ lenzen be destroyed.
- This profiling of the heat transfer walls, which are located between the fluid flows flowing in countercurrent, is structured transversely to the flow directions and is wave-like or partially circular or curvilinear in cross-section in such a way that on the two opposite sides, they delimit the heat-supply fluid channel on the surface Heat transfer walls in the profile section of partially circular or
- the two large-area outer walls of the two heat transfer fluid plates which are identical to the two large area outer walls of the three-channel heat exchanger plate described above, can be used for greater turbulence in the heat transport fluid flow, which promotes heat absorption. is also to be profiled, in particular, in a wave-like manner transversely to the direction of flow.
- the wave-like or part-circular or curvilinear profiling is dimensioned such that the specific length of one meter of the heat supply fluid
- 2 ⁇ channels depending on the type of profile and especially in the case of the combination of cylindrical and cuboidal flow spaces, has approximately seven to nine cylindrical and correspondingly cuboidal flow spaces lying transversely to the direction of flow.
- cylindrical flow spaces is about five to seven centimeters and corresponding to the diameter about ten to fourteen centimeters.
- the specific length of one meter (Im) of the heat supply fluid channel also has about seven to nine now columnar flow spaces .
- the diameter of the cross section of the cylindrical portion of this columnar space is also about ten to fourteen centimeters.
- the outer radius of the cross sections of these columns, which runs through the lateral edge intersections of the column cross sections, is between approximately five and twelve centimeters, depending on the type of profile.
- the successive, transverse C flow spaces can also be arranged offset from one another, whereby additional reversals are introduced.
- This principle of the lateral displacement of the flow spaces or the asymmetrical displacement of the passages can be applied to all types of wave-like or partially circular or curved profile, that is also to the profile type with only one type of columnar flow spaces and the pointed, angular profile ribs.
- the cheapest profile of all different possible, more or less special profiles is the j C ⁇ point symmetrical, standard corrugated sheet. With this profiling, there are round profile ribs on the surfaces of the heating duct walls and also only one type of transverse, columnar flow spaces. _0
- Profiled pipes have the disadvantage in comparison to profiled plate channels that they have a lower capacity in relation to the mass flow to be implemented and are accordingly more expensive in terms of material and processing.
- the three-channel heat exchanger plate according to the invention is preferably installed in an approximately horizontal position, but in principle vertical installation is also possible.
- the described components of the three-channel mecanical plate, the two heat transfer fluid plates, of which one side forms the partition wall for internal heat supply fluid passage may inexpensive high quality incorporating square ⁇ "" and long lifetime can be produced.
- the device according to the invention in the simplest case, for example, approximately 3 mm thick steel sheets are obtained which are given their ready-to-install shape by simple bending and folding.
- the lateral sealing of the plate-shaped channels takes place during the manufacture of the heat exchanger by welding and / or with the aid of the same or different side plates or plate-shaped pieces which can be screwed on, welded on or otherwise tightly fastened.
- the desired length is then cut from this "endlessly" profiled sheet metal, bent as required by the 180 ° deflections and laterally between
- the profiling is also carried out in the 180 ° deflection area in such a way that the profiling is "endless"
- One of the side plates can preferably be removed from the heat exchanger construction, so that the heat supply fluid channel can be opened laterally during maintenance and when
- a variant of the heat exchanger described is when the heat exchanger is designed such that it can be opened laterally by means of a vertically running separating seam, and in this state the heat transfer fluid plates are laterally
- plastic or ceramics as a material for the production can be provided with profiled or non-profiled heat transfer walls, e.g. when used as a corrosion-resistant primary metal or ceramic heat exchanger operated below the dew point or when used
- the heat exchanger according to the invention is preferably connected downstream of a heating or combustion chamber into which the hot fluid is introduced or in which it is obtained by combustion.
- the preferably lying columnar combustion chamber of the boiler is preferably surrounded by a water-carrying cylindrical, cuboid or otherwise columnar jacket.
- connection of the combustion chamber to the plate-shaped heating gas channel of the heat exchanger is preferably carried out by means of a channel-shaped connector which is trapezoidal in the frontal longitudinal section or rectangular or otherwise of a similar type in the front longitudinal section.
- connection of the water-carrying jacket of the combustion chamber to the heat transfer fluid plates, the two water-carrying plates of the three-channel heat exchanger plate described above is carried out via channel-shaped connecting pieces in the frontal longitudinal section or rectangular in the frontal longitudinal section and / or with the aid of connecting pipes or other connecting pieces.
- a pressure sensor I 5 ⁇ for the generation of a control or regulating signal is installed in a primary boiler, which is connected directly or indirectly to a primary boiler heat exchanger, for regulating the mass flow of the heat supply fluid in the interior of the heat supply fluid channel.
- the heat exchanger according to the invention can therefore also be used as a condenser in heating systems, whereby it consists of
- FIG. 1 is a schematic, lateral longitudinal section through a boiler with a heat exchanger according to the invention
- FIG. 2 shows a schematic, lateral longitudinal section through a further embodiment of a heat exchanger according to the invention used in a heating boiler
- FIG. 3 is a schematic, lateral longitudinal section through a third embodiment of a heat exchanger according to the invention applied in a boiler, s ⁇
- FIG. 4 shows a schematic longitudinal section through a fourth or fifth or sixth embodiment of a heat exchanger according to the invention used in a boiler
- Fig. 5 is a schematic section through a boiler according to FIG. 1 along the line V-V.
- the heating boiler heat exchanger shown in FIG. 1 consists of the heating boiler heat exchanger head consisting of a cylindrical combustion chamber 1, and of a water-conducting jacket space 2 surrounding the combustion chamber with attached return pipe socket and burner flange and of the heat exchanger 43 or 44 and 1Q according to the invention from the channel-shaped connecting piece 32 between the boiler heat exchanger head and the heat exchanger 43 or 44 according to the invention.
- the heating gases generated in the combustion chamber 1 pass through the heating gas channel 32a of the channel-shaped connecting piece 32 into the plate-shaped heating gas channel 3, the inner channel of the three-channel heat exchanger plate 43, and pass through the three 180 "deflections 7 on their way through the heating gas channel. 8 and 9 until they emerge from the exhaust pipe narrowing to the pipe.
- the heat transport fluid here water, flows via the connecting pipe 26 and the subsequent branching into the two separate or laterally connected heat transport fluid plates 10 and 11, each consist of two sheet-like sheets and an enclosed heat transfer port fluid flow channel and which limit the internal heating gas channel 3 up and down and in the case of the edge-side connection of the two heat transfer fluid plates 10 and 11, the heating gas channel 3 not only at the top and bottom but also at least surrounded on one edge.
- the two heat transfer fluid plates 10 and 11 bent three times by 180 ° form the two outer structural components of the three-layer heat exchanger plates 43 and 44 bent three times by 180 ".
- FIG. 1 thus shows three 180 ° deflections 45 of the three-channel, here three times bent heat exchanger plate 44.
- insulating spaces 24 are present between the vertically superposed floors of the heat exchanger plate 43, which are provided with insulating material e.g. Mineral wool can be filled.
- insulating material e.g. Mineral wool
- FIG. 1 The construction shown in FIG. 1 is given additional stability by the sheet metal strips 25 used.
- FIG. 1 shows the basic element of the heat exchanger 43 according to the invention, here a three-channel heat exchanger plate 44 bent three times by 180 °, that is to say having the 2Q three 180 "deflections 45, which has two heat transport fluid plates 10 and 11 as construction components which are made of plan, non-profiled, only in the deflection area bent steel sheets.
- the embodiment shown in FIG. 2 shows heat transfer walls 27 of the heat transfer fluid plates 10 and
- 2_C channel 3 is in turn limited by the profiled heat transfer walls 27, which are the walls of the heat transfer fluid plates 10 and 11 facing the heating gas channel 3.
- differently sized flow spaces are located in the heating gas duct, namely larger, cylindrical
- FIG. 4 Such an example of a cross-sectionally circular or curvilinear profile is shown in FIG. 4 with profiled heat transfer walls 42. Point 47 marks the single-edged, pointed profile rib in this profile.
- the walls 29 of the heat transfer fluid plates 10 and 11 facing away from the heating gas channel are also profiled C ⁇ namely wave-like, so that an optimal, turbulent flow behavior of the heat transfer fluid is generated.
- the profiling can run on both walls of the two heat transport fluid plates 10 IQ and 11, which is not shown in the exemplary embodiment in FIG. 3.
- the load-bearing structure corresponds to that shown in FIG. 2. Otherwise, three different profiles of the heat transfer walls that limit the plate-shaped heating gas channel are shown in FIG.
- the heat transfer walls 42 are profiled in a partially circular or curvilinear cross-section such that single-edged, pointed profile ribs 47 and only one type of columnar flow spaces 49 occur in the plate-shaped heating gas channel.
- the heat transfer walls 40 have a wave-like profile with blunt, round profile ribs 41 and also only one type of columnar heating gas channel flow spaces 39.
- the heat transfer walls 48 show a profile in which the smaller heating channel flow spaces 30 are vertically offset from the larger 31.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AU13690/97A AU1369097A (en) | 1995-12-11 | 1996-12-08 | Heat exchanger |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE1995146190 DE19546190C1 (de) | 1995-12-11 | 1995-12-11 | Wärmetauscher |
DE19546190.8 | 1995-12-11 |
Publications (2)
Publication Number | Publication Date |
---|---|
WO1997021968A2 true WO1997021968A2 (de) | 1997-06-19 |
WO1997021968A3 WO1997021968A3 (de) | 1997-07-24 |
Family
ID=7779796
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP1996/005491 WO1997021968A2 (de) | 1995-12-11 | 1996-12-08 | Wärmetauscher |
Country Status (3)
Country | Link |
---|---|
AU (1) | AU1369097A (de) |
DE (1) | DE19546190C1 (de) |
WO (1) | WO1997021968A2 (de) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10158148A1 (de) * | 2001-07-05 | 2003-02-27 | Ruhrgas Ag | Warmwasserbereiter für Brauch- und Heizungswasser |
DE102010010671A1 (de) | 2010-03-08 | 2011-09-08 | David Breen | Waermetauscher |
NL2012066C2 (nl) | 2014-01-09 | 2015-07-13 | Intergas Heating Assets B V | Warmtewisselaar, werkwijze voor het vormen daarvan en gebruik daarvan. |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1805165A (en) * | 1930-02-14 | 1931-05-12 | Louis S Denney | Hot water heater |
EP0123994A1 (de) * | 1983-04-28 | 1984-11-07 | Etablissement Agura | Kondensatheizkessel mit einem mäanderförmigen Wärmeaustauschteil |
DE8220601U1 (de) * | 1982-07-19 | 1987-12-10 | Weigelt, Arno-Wolfgang, Ing.(Grad.), 7250 Leonberg | Wärmetauscher |
DE3912628A1 (de) * | 1989-04-18 | 1990-10-25 | Helmut Zink | Waermetauscher |
Family Cites Families (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE3602608A1 (de) * | 1986-01-29 | 1987-07-30 | Wahler Gmbh & Co Gustav | Rohrwaermetauscher |
DE4140953A1 (de) * | 1991-12-12 | 1993-06-17 | Richard Vetter | Fuer warmwasserheizkessel bestimmter roehrenwaermetauscher |
-
1995
- 1995-12-11 DE DE1995146190 patent/DE19546190C1/de not_active Expired - Fee Related
-
1996
- 1996-12-08 WO PCT/EP1996/005491 patent/WO1997021968A2/de active Application Filing
- 1996-12-08 AU AU13690/97A patent/AU1369097A/en not_active Abandoned
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1805165A (en) * | 1930-02-14 | 1931-05-12 | Louis S Denney | Hot water heater |
DE8220601U1 (de) * | 1982-07-19 | 1987-12-10 | Weigelt, Arno-Wolfgang, Ing.(Grad.), 7250 Leonberg | Wärmetauscher |
EP0123994A1 (de) * | 1983-04-28 | 1984-11-07 | Etablissement Agura | Kondensatheizkessel mit einem mäanderförmigen Wärmeaustauschteil |
DE3912628A1 (de) * | 1989-04-18 | 1990-10-25 | Helmut Zink | Waermetauscher |
Also Published As
Publication number | Publication date |
---|---|
AU1369097A (en) | 1997-07-03 |
WO1997021968A3 (de) | 1997-07-24 |
DE19546190C1 (de) | 1997-04-24 |
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