EP2573480B1 - Dispositif de chauffage d'un caloporteur, en particulier pour machines de laverie - Google Patents

Dispositif de chauffage d'un caloporteur, en particulier pour machines de laverie Download PDF

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Publication number
EP2573480B1
EP2573480B1 EP12006484.5A EP12006484A EP2573480B1 EP 2573480 B1 EP2573480 B1 EP 2573480B1 EP 12006484 A EP12006484 A EP 12006484A EP 2573480 B1 EP2573480 B1 EP 2573480B1
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EP
European Patent Office
Prior art keywords
heat exchanger
flow channel
heat
longitudinal
cylindrical
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.)
Active
Application number
EP12006484.5A
Other languages
German (de)
English (en)
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EP2573480A2 (fr
EP2573480A3 (fr
Inventor
Wilhelm Bringewatt
Engelbert Heinz
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.)
Herbert Kannegiesser GmbH and Co
Original Assignee
Herbert Kannegiesser GmbH and Co
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Filing date
Publication date
Application filed by Herbert Kannegiesser GmbH and Co filed Critical Herbert Kannegiesser GmbH and Co
Publication of EP2573480A2 publication Critical patent/EP2573480A2/fr
Publication of EP2573480A3 publication Critical patent/EP2573480A3/fr
Application granted granted Critical
Publication of EP2573480B1 publication Critical patent/EP2573480B1/fr
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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
    • F24H1/43—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water tube or tubes helically or spirally coiled
    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F58/00—Domestic laundry dryers
    • D06F58/20—General details of domestic laundry dryers 
    • D06F58/26—Heating arrangements, e.g. gas heating equipment
    • D06F58/263—Gas heating equipment
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/12—Radiant burners
    • F23D14/125—Radiant burners heating a wall surface to incandescence
    • 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
    • F24H1/406—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water tube or tubes the tubes forming a membrane wall
    • D—TEXTILES; PAPER
    • D06—TREATMENT OF TEXTILES OR THE LIKE; LAUNDERING; FLEXIBLE MATERIALS NOT OTHERWISE PROVIDED FOR
    • D06F—LAUNDERING, DRYING, IRONING, PRESSING OR FOLDING TEXTILE ARTICLES
    • D06F39/00—Details of washing machines not specific to a single type of machines covered by groups D06F9/00 - D06F27/00 
    • D06F39/04—Heating arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2203/00—Gaseous fuel burners
    • F23D2203/005—Radiant burner heads
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2203/00—Gaseous fuel burners
    • F23D2203/10—Flame diffusing means
    • F23D2203/101—Flame diffusing means characterised by surface shape
    • F23D2203/1012—Flame diffusing means characterised by surface shape tubular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2203/00—Gaseous fuel burners
    • F23D2203/10—Flame diffusing means
    • F23D2203/103—Flame diffusing means using screens
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2203/00—Gaseous fuel burners
    • F23D2203/10—Flame diffusing means
    • F23D2203/106—Assemblies of different layers

Definitions

  • the invention relates to a device for heating a heat carrier for laundry machines in particular according to the preamble of claim 1.
  • Heat carriers in particular heat transfer fluids, such as thermal oil, are used to supply the heat required to machines that work with heat.
  • laundry machines such as dryers, washing machines, ironers or the like are supplied with the required heating energy via heat transfer media.
  • heat transfer media are heated in devices that have at least one burner and at least one heat exchanger. The heat transfer medium is heated as it flows through the heat exchanger or a plurality of heat exchangers by the energy supplied to the respective heat exchanger by the flames of the burner.
  • a device for heating a heat carrier in which the flame of a burner is surrounded by a heating tube.
  • a heat exchanger is provided around the heating tube and has tubes.
  • the heating tube fired from the inside is designed to generate heat radiation acting on the heat exchanger.
  • the tubes of the heat exchanger are heated by the flue gas from the burner emerging from the heating tube.
  • a burner with a tubular burner element which has a gas-permeable outer surface. Fuel gas is blown into the interior of the burner element and exits radially outward through the gas-permeable wall of the burner element, where it is ignited by an ignition device provided next to the burner element.
  • the EP 2 149 636 A1 discloses a device for heating a heat transfer medium for laundry machines in particular with two double-walled, cylinder-like heat exchangers. An internal heat exchanger is fired directly by a flame from a burner.
  • the invention has for its object to provide a device for heating a heat carrier for laundry machines in particular, which has a good thermal efficiency with low emissions.
  • a device for solving this problem has the features of claim 1.
  • this device it is provided to arrange a heating tube fired from the inside by the burner in order to generate heat radiation in the interior enclosed by the tubular heat exchanger.
  • the heating tube is designed to emit radially outward radiation. This radiation is oriented radially in such a way that it is directed onto the inner heat exchanger surface of the heat exchanger surrounding the heating tube.
  • the heating tube is designed in such a way that the outer lateral surface emits radially outwardly directed infrared rays and these infrared rays transmit their energy to the heat exchanger surface of the heat exchanger surrounding the heating tube.
  • This type of energy transmission by infrared radiation leads to a particularly economical and environmentally friendly heating of a heat carrier with at least one heat exchanger and is characterized by good thermal efficiency. It also has low emissions.
  • the device according to the invention thus works economically and in an environmentally friendly manner.
  • the heating tube has a perforated or grid-like support tube for the at least one mantle.
  • the heating tube is essentially formed from the support tube and the mantle.
  • the mantle is pulled onto the support tube from the outside, so that the perforated or grid-like support tube supports the mantle, which is elastic or pliable as a result of its woven, braid or grid structure, and thereby gives it the preferably cylindrical shape of the support tube and ensures that the respective one Glow sock maintains this shape even when heated or glowing.
  • the heating tube has at least one mantle made of a heat-resistant fabric, braid and / or grid.
  • a mantle is heated from the inside by means of the flames of the burner, preferably made to glow, the fabric, braid and / or grid for the formation of the mantle preventing the passage of flames at least partially or for the most part, preferably entirely.
  • the glow sock is red-hot on the outside of at least one heat exchanger, whereby it generates infrared rays.
  • the energy of the infrared rays is emitted to the heat exchanger surrounding the mantle at a distance, namely at least one inner heat exchanger surface thereof, this energy heating the heat transfer medium, in particular heat transfer fluid, flowing through the heat exchanger.
  • a high-temperature-resistant metal and / or high-temperature-resistant ceramics are preferably considered as the material for forming the mantle. It is then a matter of metal or ceramic fibers and / or strands or threads.
  • the materials mentioned are characterized by a long service life in the glowing or very hot state.
  • the materials are suitable for forming a stable and durable braid, fabric, net or even a nonwoven that, when exposed to flames on one side, emits heat radiation, in particular infrared rays, on the other side, without the flames of the burner step through the mantle.
  • the at least one cylinder-like heat exchanger is double-walled, the longitudinal edges of both walls of the cylindrical heat exchanger being connected by a longitudinal weld seam and the longitudinal weld seam partially delimiting at least part of at least one flow channel in the double-walled, cylinder-like heat exchanger.
  • Such a heat exchanger is particularly advantageously suitable for forming the device described in the introduction, in which the flames of the burner heat up at least one heating tube arranged in the interior enclosed by the tubular heat exchanger and on the outside of the heating tube the energy generated by the flames is generated by radiation, in particular infrared radiation the at least one heat exchanger is transferred.
  • the heat exchanger is preferably designed as a double-walled heat exchanger with at least one flow channel created by hydraulic expansion.
  • such a heating tube is assigned to only one, preferably internal, heat exchanger.
  • the heating tube is heated directly from the inside by the flames of the burner. However, the flames are retained by the heating pipe, so that the outside of the heating pipe heated by the flames emits radiation energy to the heat exchanger surrounding the heating pipe.
  • a preferred embodiment of the device provides for the heating tube to be provided with an inner diameter which allows the flames of the burner to extend through the heating tube with the at least one glow sock supported by it.
  • the flames can heat the heating tube, in particular the at least one glow sock arranged thereon, directly from the inside and thereby bring the at least one glow sock to glow if necessary.
  • the heating tube with the mantle is thus used as a means for converting the flames into radiation to be emitted by the mantle, in particular infrared radiation, for heating the heat carrier in at least one heat exchanger.
  • the at least one tubular heat exchanger concentrically surrounds the heating tube with the mantle, the inner diameter of the at least one heat exchanger being larger than the outside diameter of the heating tube or mantle, so that the at least one heat exchanger surrounds the mantle at a distance .
  • each flow channel in the interior of the double-walled, tubular heat exchanger in particular a single, continuous flow channel, is formed from a plurality of parallel flow channel sections which run in the circumferential direction of the cylindrical heat exchanger and through overflow sections at their end regions lying on both sides of the longitudinal seam are connected.
  • the heating of the heat transfer medium is particularly uniform when the heat exchanger is heated by radiation emitted by the heating tube, in particular infrared radiation.
  • the at least one flow channel preferably a single continuous flow channel
  • the heat transfer medium flows in a laminar, namely longitudinally, through the cylindrical heat exchanger, and also in a zigzag from one flow channel section to the other.
  • the longitudinal weld seam practically has no influence on the design and the course of the flow channel, but the longitudinal weld seam forms a boundary between adjacent longitudinal flow channel sections running between two parallel longitudinal flow channel sections.
  • the devices shown in the figures are used to heat or heat a heat transfer medium.
  • the heat transfer medium is preferably a heat transfer fluid with a high boiling point.
  • the heat transfer medium is used to supply thermally working machines, in particular laundry machines, with thermal energy.
  • the devices shown in the figures are particularly suitable for supplying dryers, washing machines, in particular continuous washing machines, and ironers for commercial laundries.
  • the 1 to 12 each show devices with a two-pass, cylindrical heat exchanger 20.
  • the cylindrical inner wall and the cylindrical outer wall of the heat exchanger 20 each form a heat exchanger surface, so that energy can be supplied to the heat exchanger 20 from both sides.
  • the heat exchanger 20 is supplied with energy which is generated by a gas or oil-heated burner 21. If necessary, the device can also have a plurality of burners 21.
  • the only cylindrical heat exchanger 20 in the embodiment shown is double-walled.
  • the device has a preferably cylindrical housing 22 which surrounds the heat exchanger 20.
  • the diameter of the housing 22 is so much larger than the outer diameter of the heat exchanger 20 that an outer annular space 23 is formed between the heat exchanger 20 and the housing 22.
  • Outer end walls 24, 25 of the housing 22 are spaced from the ends of the cylindrical heat exchanger 20 which are open at the end faces, as a result of which the outer annular space 23 around the heat exchanger 20 is connected to an inner cylinder space 26 surrounded by the heat exchanger 20.
  • the burner 21 is assigned to the end wall 25 in that the burner 21 is connected to the end wall 25 with a releasable flange connection.
  • a heating tube 27 is provided concentrically in the cylinder space 26 enclosed by the heat exchanger 20.
  • the heating tube 27 is connected to the burner 21 at one end. Another, preferably closed, free end 29 of the heating tube terminates approximately flush with the open end face of the heat exchanger 20. As a result, the free end 29 of the heating tube 27, like the open end of the heat exchanger 20, is spaced apart from the end wall 24 of the housing 22 of the device.
  • the heating tube 27 serves to be heated by the flames of the burner 21.
  • the flames of the burner 21 are passed through the interior of the heating tube 27.
  • the flames in the interior of the heating tube 27 heat the outside, in particular the outer lateral surface thereof.
  • the energy is emitted from the hot outer lateral surface of the heating tube 27 by heat radiation, in particular infrared radiation.
  • the heating tube 27 has an inner support tube 30 and at least one glow sock 32 drawn onto the support tube 30.
  • the glow sock 32 thus surrounds the entire support tube 30.
  • the support tube 30 is provided with openings 31 in its outer surface ( Fig. 3 ).
  • the distribution of the openings 31 over the lateral surfaces of the support tube 30 is selected such that a uniform heat distribution over the circumference and the length of the support tube 30 is achieved.
  • the total area of the openings 31 corresponds to a part of the total area of the support tube 30.
  • the glow sock 32 is formed from a fabric, braid, fleece or a grid.
  • the fabric, braid, fleece or the like consist of highly heat-resistant fibers, strands or threads made of a corresponding metal or ceramic. It is also conceivable to form the mantle 32 from a steel / ceramic mixture, in that the fabric or braid is produced both from ceramic fibers or strands and from metal fibers or strands.
  • the glow sock 32 can be formed from a single or multi-layer fabric made of metallic and / or ceramic fibers or strands. It is crucial that the flames of the burner 21 flowing through the interior of the heating tube 27 do not or only to a small extent escape through the mantle 32. The flames of the burner 21 are thus retained by the mantle 32.
  • the flames of the burner 21 thus only heat the mantle 32 by at least causing the metallic fibers and strands to form the mantle 32 to glow.
  • the heat energy is emitted by radiation from the warmed or glowing cylindrical outer surface of the mantle 32.
  • the mantle 32 preferably emits infrared rays on its outer circumference.
  • the rays, in particular infrared rays are essentially radial directed outside, namely against the inside of the heat exchanger 20.
  • the radiant heat generated by the heating tube 27, in particular infrared radiation is thus transmitted to the inner heat exchanger surface of the heat exchanger 20.
  • the flue gases of the burner 21 emerge from the entire outer surface of the heating tube 27.
  • the flue gases can flow along the outside of the heat exchanger 20.
  • the flue gases leave the housing 22 through a flue gas outlet 33.
  • air circulation is created by a chimney effect along the inner heat exchanger surface of the heat exchanger 20 opposite the mantle 32 and along the outer heat exchanger surface.
  • the hot air on the inner heat exchanger surface flows in the longitudinal direction of the heat exchanger 20 towards the end wall 24 of the housing 22 and from there along the outside of the heat exchanger 20 towards the end wall 25, from where the air leaves the housing 22 through the flue gas outlet 33 .
  • the heat exchanger 20 is double-walled.
  • the two walls formed from flat sheets 35 or plates are connected to one another in regions, namely welded.
  • the regions of the walls of the heat exchanger 20 which are not connected to one another are then hydraulically expanded by introducing a liquid under high pressure, as a result of which the flow channel 34 is formed in the interior of the double-walled heat exchanger 20.
  • the Fig. 5 shows a top view of the still flat, rectangular cut of two sheets 35 lying one above the other to form the heat exchanger 20 .
  • the sheets 35 are liquid-tight all around.
  • a large number of parallel connecting seams 38 is provided in the area of the surface of the metal sheets 35.
  • the connecting seams 38 run parallel to the transverse edges 37 and thus radially in the circumferential direction of the cylindrical heat exchanger 20 formed from the sheets 35.
  • the sheets 35 are connected to one another continuously as a longitudinal seam or partially by interrupted longitudinal seams.
  • the connecting seams 38 are alternately connected to one or the other longitudinal edge 36 ( Fig. 5 ). Adjacent connecting seams 38 thus end at a distance in front of one longitudinal edge 36 or the other longitudinal edge 36.
  • a single continuous flow channel 34 is thus created with a zigzag shape or serpentine course.
  • the connecting seams 38 or the transverse edges 37 delimit flow channel sections running transversely to the longitudinal direction of the heat exchanger 20, an overflow section being located where the respective connecting seam 38 ends at a distance from the respective longitudinal edge 36, whereby the heat carrier flowing through the flow channel 34, in particular the heat transfer fluid is deflected from a radial flow channel section to the adjacent radial flow channel section.
  • the two plates or sheets 35 of the same thickness with a thickness between 0.5 mm and 3 mm, preferably 1 mm to 2 mm, of steel, in particular stainless steel, are welded together to form the flow channel 34, the two plates which are connected to one another in regions or sheets 35 rounded so that a cylindrical tube is formed.
  • the two longitudinal edges 36 of the connected sheets 35 which form a longitudinal seam of the tube, are connected to one another by a longitudinal weld seam 39, so that a closed tube is formed to form the tubular heat exchanger 20 ( Fig. 4 ).
  • Areas of the sheets 35 between the weld seams which are not hydraulically connected to one another are then widened to form the flow channel 34 running in a zigzag or serpentine fashion in the tubular heat exchanger 20.
  • the 6 and 7 show a device that differs from that of 1 to 5 only differs in that the likewise tubular heat exchanger 40 for forming the flow channel 41 between the plates or sheets 35 instead of with continuous connecting seams 38 according to the embodiment of FIG 1 to 5 is formed by several rows of weld spots 42.
  • Several parallel rows of welding points 42 run parallel to the transverse edge 37, in exactly the same way as the connecting seams 38.
  • the approximately equal distances between the welding points 43 of each row of welding points 42 are smaller than the distance between two adjacent rows of welding points 42 or the respective transverse edge 37 and the adjacent one Welding spot row 42.
  • the flow channel 41 is formed in the double-walled heat exchanger 40, which, as in the embodiment of FIG 1 to 5 has a zigzag-shaped or serpentine course, which in turn creates adjacent radially circumferential flow channel sections. Because each row of welding points 42 alternately ends at a greater distance from a longitudinal edge 36, overflow channels between adjacent flow channel sections are in turn formed. In a departure from the exemplary embodiment described, other distributions of the welding points 43 are conceivable - even without rows of welding points 42. Also with the heat exchanger 40 Fig. 6 and 7th are the longitudinal edges 36 of the sheets 35 after rounding to a tube with a longitudinal weld. The device with the heat exchanger 40 is designed in exactly the same way as the device in FIG 1 to 5 . The device works the same way.
  • the 8 and 9 show a device which differs from those of the previously described exemplary embodiments only by a differently designed heat exchanger 44.
  • the heat exchanger 44 is also cylindrical and double-walled.
  • In the heat exchanger 44 there is a single flow channel 45 which runs continuously in the double-walled heat exchanger 44 in the manner of a spiral or helix.
  • the flow channel 45 is delimited on both sides by an uninterrupted helical circumferential connecting seam 46, which is formed either as an uninterrupted longitudinal seam or as a row of welding points from a multiplicity of individual, spaced-apart welding points.
  • the cylindrical heat exchanger 44 of this exemplary embodiment does not have a longitudinal weld seam 39. Instead, the heat exchanger 44 is formed from helically wound double-layer strips which are connected at their edges that run helically around the longitudinal central axis 28 of the cylindrical heat exchanger 44 by a circumferential helical or helical passage weld seam 47 which can also form the connecting seam 46 at the same time.
  • the heat exchanger 44 also serves to form a device according to FIGS 1 to 5 . He works the same way.
  • the 10 to 12 show a further embodiment of the device, which in turn differs from the previously described devices only by a differently designed heat exchanger 48.
  • the heat exchanger 48 is also designed as a cylindrical, double-walled heat exchanger 48.
  • Several parallel, identical flow channels 49 are arranged in the heat exchanger 48.
  • the flow channels 49 run in the longitudinal direction of the heat exchanger 48, that is to say parallel to its longitudinal central axis 28.
  • the double-walled heat exchanger 48 is also made of two parallel, equally large flat plates or sheets 35 made of steel or stainless steel with the same thickness between 0.5 mm to 3 mm, in particular 1 mm to 2 mm, formed.
  • the parallel longitudinal edges 50 and the parallel transverse edges 51 of the two sheets 35 of the same thickness are connected to one another in a liquid-tight manner by means of continuous weld seams.
  • rectilinear connecting seams 52 are provided between the longitudinal edges 50 and run parallel to them.
  • the connecting seams 52 are spaced from one another or from the respective longitudinal edge 50 in such a way that a flow channel 49 of the desired size is formed between them.
  • the connection seams 52 can be formed by continuous longitudinal weld seams or rows of weld spots.
  • the connecting seams 52 each end at a distance in front of both transverse edges 51 of the two sheets 35 to form the heat exchanger 48 ( Fig. 12 ).
  • all flow channels 49 are open at opposite ends for the entry and exit of the heat carrier flowing through the flow channels 49 in the longitudinal direction.
  • the heat transfer medium is fed to the heat exchanger 48 on one end face and discharged on the other end face of the cylindrical heat exchanger 48.
  • two feed lines 53 on one end face and two discharge lines 54 for heated or heated heat transfer media on the other end face of the heat exchanger 48 serve this purpose, in the exemplary embodiment shown on the end face to which the burner 21 is assigned.
  • the heat exchanger 48 is manufactured in a similar way to the heat exchanger 20. After the sheets 35 or plates have been welded in the flat state, the sheets 35 which are welded together and connected in this way at certain points are rounded to form the cylindrical heat exchanger 48. The longitudinal edges 50 are then, as in the case of the heat exchanger 20 a longitudinal weld 39 running parallel to the longitudinal central axis 28 of the cylindrical heat exchanger 48 is welded. After the longitudinal weld seam 39 has been produced, the flow channels 49 of the heat exchanger 48 are formed by hydraulic widening of the plates 35 in the regions of the superimposed plates 35 which are not connected to one another. This is preferably done in turn by introducing a liquid under high pressure.
  • the heat exchanger 48 serves to form a device that corresponds to that used in connection with the first exemplary embodiment of FIG 1 to 5 has been described. The way it works is the same.
  • the 13 to 15 show a further embodiment of the invention with two cylindrical, double-walled heat exchangers 55, 56.
  • the heat exchangers 55, 56 are of different sizes.
  • the heating tube 27 is surrounded by the smaller diameter heat exchanger 56.
  • This heat exchanger 56 is surrounded by the larger diameter heat exchanger 55.
  • Both heat exchangers 55 and 56 are arranged coaxially to one another so that their longitudinal axes, like the longitudinal axis of the heating tube 27, lie on a common axis, namely the longitudinal central axis 28 of the housing 22 of the device.
  • the diameters of the heat exchangers 55 and 56 differ so much from one another that a central annular space 57 is formed between the cylindrical heat exchangers.
  • An outer annulus 58 is located between the outer, larger heat exchanger 55 and the housing 22.
  • An inner annulus 59 is formed between the cylindrical outer surface of the mantle 32 of the heating tube 27 and the inner heat exchanger surface of the smaller (inner) heat exchanger 56.
  • the housing 22 has a central flue gas outlet 60 in the end wall 24 opposite the burner 21.
  • the inner, smaller heat exchanger 56 is shorter than the outer, larger heat exchanger 55.
  • the open end face of the cylindrical smaller heat exchanger 56 is set back from the open end face of the larger heat exchanger 55.
  • the open end faces of both heat exchangers 55, 56 lie in a common plane which is spaced apart from the end wall 25.
  • the open end of the larger diameter heat exchanger 55 is also from the opposite end wall 24 with the flue gas outlet 60 spaced.
  • the heat exchangers 55 and 56 are designed in the same way, and indeed their flow channels.
  • the tubular heat exchangers 55, 56 is also provided with a longitudinal weld 61, 62 ( Fig. 14 ). This connects the two plates or sheets 35 to form the double-walled heat exchangers 55, 56 and the longitudinal edges of the plates or sheets 35.
  • the Fig. 15 shows an alternative embodiment of the device of FIG 13 and 14 with a three-way heat exchange. Only here there is a single heat exchanger 63 which, by means of a two-circuit spiral rounding, the inner annular space 59, the central annular space 57 and the outer annular space 58 between the heat exchanger 63 and that in FIG Fig. 15 Housing 22 not shown receives.
  • the longitudinal edges 64, 65 in the heat exchanger 63 are not connected to one another. Both longitudinal edges 64, 65 lie on a central longitudinal plane of the heat exchanger 63, but at different distances from the central longitudinal axis 28 ( Fig. 15 ).
  • heat exchanger 63 there can also be only a single flow channel, which is formed in exactly the same way as in the heat exchangers 55 and 56 or in the heat exchanger 20.
  • the three-pass heat exchangers 55, 56 and 63 can also be designed like the heat exchangers 20, 40, 44 or 48.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Textile Engineering (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Drying Of Solid Materials (AREA)

Claims (8)

  1. Dispositif de chauffage d'un fluide caloporteur destiné à des lave-linge, le dispositif comprenant notamment un brûleur (21) auquel est associé un tube chauffant (27) à chauffage interne et au moins un échangeur de chaleur (20, 40, 44, 48, 55, 56, 63) qui comporte au moins un conduit d'écoulement (34, 41, 45, 49) destiné au fluide caloporteur, le tube chauffant (27) générant un rayonnement thermique agissant sur l'échangeur de chaleur (20, 40, 44, 48, 56, 63), le tube chauffant (27) qui est disposé dans un espace cylindrique (26) enfermé par l'au moins un échangeur de chaleur cylindrique (20, 40, 44, 48, 55, 56, 63) et qui est chauffé de l'intérieur par le brûleur (21) étant conçu pour délivrer un rayonnement infrarouge dirigé radialement vers l'extérieur par rapport à l'au moins un échangeur de chaleur (20, 40, 44, 48, 56, 63), caractérisé en ce que l'au moins un échangeur de chaleur (5) est à double paroi, en ce que le tube chauffant (27) comporte un tube de support (30) perforé ou en réseau et au moins un manchon à incandescence (32) formé d'un tissu, d'une tresse et/ou d'un treillis résistant à la chaleur, l'au moins un manchon à incandescence (32) entourant le tube de support (30) depuis l'extérieur, et en ce que l'au moins un échangeur de chaleur (20, 40, 44, 48, 55, 56) comporte une paroi intérieure cylindrique et une paroi extérieure cylindrique qui forment des surfaces d'échangeur de chaleur destinées à alimenter en énergie des deux côtés l'au moins un échangeur de chaleur (20, 40, 44, 48, 55, 56), des bords longitudinaux (36) des deux parois de l'au moins un échangeur de chaleur cylindrique (20, 40, 44, 48, 55, 56) étant reliés par au moins un cordon de soudure longitudinal (39, 61) pour former une partie de l'au moins un conduit d'écoulement (34, 41, 45, 49) à travers l'au moins un cordon de soudure longitudinal (39, 61).
  2. Dispositif selon la revendication 1, caractérisé en ce que la tresse, le tissu et/ou le treillis du manchon à incandescence (32) est formé de brins ou fibres résistants aux hautes températures de préférence en métal et/ou en céramique.
  3. Dispositif selon la revendication 1, caractérisé en ce que le manchon à incandescence (32) est tiré sur le tube de support (30).
  4. Dispositif selon l'une des revendications 2 ou 3, caractérisé en ce que le tube chauffant (27) a un diamètre intérieur tel que les flammes du brûleur (21) s'étendent à travers le tube chauffant (27) entouré de l'au moins manchon à incandescence (32).
  5. Dispositif selon l'une des revendications 2 à 4, caractérisé en ce que l'au moins un échangeur de chaleur tubulaire (20, 40, 44, 48, 56, 63) est espacé du manchon à incandescence (32), de préférence l'au moins un échangeur de chaleur (20, 40, 44, 48, 56, 63) entoure concentriquement à distance l'au moins un manchon à incandescence (32).
  6. Dispositif selon la revendication 1, caractérisé en ce que l'au moins un conduit d'écoulement (34, 41) comporte une pluralité de portions de conduit d'écoulement parallèles qui s'étendent dans la direction périphérique de l'au moins un échangeur de chaleur cylindrique (20, 40, 55, 56) et qui sont reliées au niveau de leurs zones d'extrémité, situées des deux côtés du cordon de soudure longitudinal (39, 61), par des portions de trop-plein.
  7. Dispositif selon la revendication 1 ou 6, caractérisé en ce qu'au moins un conduit d'écoulement (49) comporte une pluralité de portions de conduit d'écoulement parallèles qui s'étendent parallèlement au cordon de soudure longitudinal (39) et qui sont reliées à des zones d'extrémité de l'au moins un échangeur de chaleur cylindrique (48) par des conduits de trop-plein.
  8. Dispositif selon la revendication 1, caractérisé en ce que le cordon de soudure longitudinal (39) est formé entre deux portions de conduit d'écoulement parallèles adjacentes.
EP12006484.5A 2011-09-23 2012-09-14 Dispositif de chauffage d'un caloporteur, en particulier pour machines de laverie Active EP2573480B1 (fr)

Applications Claiming Priority (2)

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DE102011114166 2011-09-23
DE102012000302.1A DE102012000302B4 (de) 2011-09-23 2012-01-10 Vorrichtung zum Aufheizen eines Wärmeträgers für insbesondere Wäschereimaschinen

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EP2573480A2 EP2573480A2 (fr) 2013-03-27
EP2573480A3 EP2573480A3 (fr) 2018-07-11
EP2573480B1 true EP2573480B1 (fr) 2020-06-10

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CN103469531A (zh) * 2013-08-09 2013-12-25 上海赛航洗涤设备有限公司 一种用于烘干机的燃气红外加热器
DE102020118781A1 (de) 2020-07-16 2022-01-20 Miele & Cie. Kg Lamellenwärmetauscher für eine Wäschebehandlungsmaschine
CN114753110B (zh) * 2022-03-25 2023-09-08 安徽省宁国市天成科技发展有限公司 一种电加热装置

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US3847536A (en) * 1972-05-08 1974-11-12 Antargaz Radiant burner operating at high temperature
US6140658A (en) * 1973-02-16 2000-10-31 Lockheed Martin Corporation Combustion heated honeycomb mantle infrared radiation

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FR1375306A (fr) 1963-09-23 1964-10-16 Ross Gmbh Vorm Joseph Meys & C Chaudière perfectionnée pour caloporteurs de chaleur à point d'ébullition élevé
GB1230766A (fr) * 1967-07-28 1971-05-05
DE3136804A1 (de) * 1981-09-16 1983-03-31 Webasto-Werk GmbH, 8031 Stockdorf Mit stroemendem brennstoff beschickter medienerhitzer
CA1241910A (fr) 1984-02-16 1988-09-13 Dirk N. Granberg Bruleur a energie rayonnante
US5687678A (en) 1995-01-26 1997-11-18 Weben-Jarco, Inc. High efficiency commercial water heater
DE59802337D1 (de) * 1997-03-24 2002-01-17 Vth Ag Mit einem brenner ausgerüsteter heizkessel
DE102008035852A1 (de) * 2008-08-01 2010-02-04 Herbert Kannegiesser Gmbh Vorrichtung zum Aufheizen eines Wärmeträgers für insbesondere Wäschereimaschinen und bevorzugte Verwendungen der Vorrichtung
US9353967B2 (en) 2010-02-03 2016-05-31 Farshid Ahmady Fluid heating apparatus

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Publication number Priority date Publication date Assignee Title
US3847536A (en) * 1972-05-08 1974-11-12 Antargaz Radiant burner operating at high temperature
US6140658A (en) * 1973-02-16 2000-10-31 Lockheed Martin Corporation Combustion heated honeycomb mantle infrared radiation

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DE102012000302B4 (de) 2022-07-14
EP2573480A2 (fr) 2013-03-27
EP2573480A3 (fr) 2018-07-11
DK2573480T3 (da) 2020-09-14
DE102012000302A1 (de) 2013-03-28

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