EP0497113B1 - Wärmetauscher zur Warmwassererzeugung mit Öl- oder Gasbrennern - Google Patents

Wärmetauscher zur Warmwassererzeugung mit Öl- oder Gasbrennern Download PDF

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Publication number
EP0497113B1
EP0497113B1 EP92100345A EP92100345A EP0497113B1 EP 0497113 B1 EP0497113 B1 EP 0497113B1 EP 92100345 A EP92100345 A EP 92100345A EP 92100345 A EP92100345 A EP 92100345A EP 0497113 B1 EP0497113 B1 EP 0497113B1
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
exchanger according
pipe coil
coil
burner
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP92100345A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0497113A1 (de
Inventor
Rainer Oberdorfer-Bögel
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.)
WAP Reinigungssysteme GmbH and Co
Original Assignee
WAP Reinigungssysteme GmbH and Co
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by WAP Reinigungssysteme GmbH and Co filed Critical WAP Reinigungssysteme GmbH and Co
Publication of EP0497113A1 publication Critical patent/EP0497113A1/de
Application granted granted Critical
Publication of EP0497113B1 publication Critical patent/EP0497113B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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

Definitions

  • the present invention relates to a heat exchanger for producing hot water using oil or gas burners, two-layer conically wound pipe layers being provided in a horizontal arrangement and the flame cone being introduced into the area of the pipe layers from one side of the heat exchanger.
  • a heat exchanger has become known.
  • a flame pot is arranged on the side opposite the burner and the burner works with its flame in the interior of this cylindrical wound tubular heat exchanger (heating coil).
  • the heating coil was flowed through by water and the water heated thereby was used for a high-pressure cleaner, see, e.g. EP-A-0 248 282.
  • the present invention is therefore based on the object of developing a tubular heat exchanger of the type mentioned at the outset such that it has a substantially longer service life with the same or higher thermal efficiency.
  • the invention is characterized in that, starting from a two-layer tubular heat exchanger, the connection between the inner and the outer tube is made via a worm-like disk which has a through hole in the center, via which the inner tube coil of the tube heat exchanger is liquid-tight with the Outer tube coil is connected.
  • a connecting nipple protrudes through the inner disk and is welded to the inner tube coil; this connection nipple in turn is designed with a sealing edge in the manner of a cutting ring screw connection solution.
  • the same cutting ring edge is formed on the opposite side on the nut, so that no additional sealing is required.
  • Such a screw connection of such a connection also has the advantage that in the event of corrosion damage which can occur after a long time, both the inner tube coil and the outer tube coil can be separated in a simple manner. This was not possible with the previous version because there was a welded connection.
  • the previously existing baffle pot is now dispensed with and instead a spirally shaped disk is provided on the end face and is intended for the liquid-tight connection between the inner coil and the outer coil.
  • This worm-like disc is also used for the flow of water from the inner winding to the outer winding and is also the centering disc for the inner tube coil to the outer tube coil.
  • This spiral-shaped plate is thus acted upon by the flame of the burner and is thereby heated to a high temperature, but this does not lead to thermal stresses because the connection between the inner and outer helix is made via cutting ring connections; Welded connections are avoided in this context.
  • the degree of heat transfer is significantly improved, because this spiral disk is directly affected by the flame, as is the vertical coiled tubing, which is practically closed on the end in this area, so that the flame touches both the spiral disk and the coiled tubing .
  • the screw connection between the inner tube helix and the outer tube helix offers the further advantage that an elongated threaded pin also serves to receive the burner jacket. This disc also serves to center the burner jacket and to hold and fasten the entire heat exchanger.
  • the entire heat exchanger is not cylindrical, but conical, that is, the tube windings of the inner and outer windings are wound on a conical core with the aim that easier removal of these tube coils (heating coils) of the conical mandrel is possible.
  • the push-off force required to push this coiled tubing off the mandrel should therefore be kept as small as possible.
  • the heat exchanger according to the invention consists of a burner protective jacket 1, which forms the entire outer housing cylindrically.
  • a front plate 2 On one end face is a front plate 2, which engages with bends 3 in the inner circumference of the protective jacket 1, 2 bolts 5 being provided on the front plate, to which the oil-blower burner is flanged.
  • the heat exchanger is held in a mounting bracket via a further two bolts 4, the mounting being carried out in the region of an elongated hole.
  • the front panel also has a cleaning opening 6 in its upper part, which is closed from the outside by two flange plates 7, the connection being established using screws 8.
  • a flame tube 12 is arranged, which extends into the front part of the heat exchanger.
  • the heat exchanger itself consists of an inner tube coil 13 and an outer tube coil 14.
  • the inner and outer tube coils are wound very closely and touch each other, whereby it is important that the gap between the adjacent tubes is not greater than 1/10 mm.
  • the tubes lying next to one another are connected to one another by welding points 15, the welding points 15 extending in the longitudinal direction of the heat exchanger and being distributed over the circumference in a diameter circumference of 120 °.
  • connection of the two coils 13, 14 via the welding points 15 and 16 thus serves to secure the positions of the coils 13 and 14. These welding points are attached during the winding process. If a tube turn has been wound, the adjacent coils are immediately welded during the winding process, thus ensuring that the diameter accuracy is guaranteed.
  • the outer tube helix 14 merges into an end tube helix 17, it being important that at the beginning of the winding process a worm disk (spiral disk) 18 is initially present, which is first clamped onto the mandrel.
  • This worm disk has an upper flange 19, over which a weld 20 is placed, which weld connects the first tube layer 21 to this disk in a liquid-tight manner. The medium thus runs into the interior 22.
  • the water runs through the outer coil 14 into the screw-shaped cavity 22, from this screw-like disk (18) via the connecting nipple 24 and the pipe nipple 25 into the pipeline 26 the inner tube coil 13.
  • the pipe 25 is welded directly into the connecting nipple 24 (welding point 27).
  • the tube 25 is bent through 90 ° and merges seamlessly without welding into the inner tube coil.
  • the water therefore goes in the direction of fall 28 into the connecting nipple 24 with the transverse bore, flows there in the direction of the fall 29 and then reaches the pipe connection 26 in the direction 30.
  • the nut 33 is connected on the end face to a threaded pin 35 which centers around the burner jacket 36, this burner jacket 36 being a pot-like housing which has a bore 37 in this area.
  • the burner jacket 36 extends towards the front towards the front plate 2, a sealing washer 38 being present and the end face 39 of the burner jacket being pressed axially onto this sealing disk 38 in that the heat exchanger is fastened on the one hand with the nut 40 to the inlet 23 and on the other hand with the nut 41 on the threaded bolt 35.
  • the front plate 2 is pressed onto the pot-shaped burner jacket 36 in the axial direction.
  • burner jacket 36 is double-walled in the lower region, as can be seen from FIG. This means that it overlaps in this area by a certain overlap path and it is a condensate drain 46 arranged to drain the resulting condensate down.
  • the flame cone 47 thus extends into the interior of the heat exchanger and then strikes the spirally formed disk 18 and the vertical tubular coil 17 arranged on the end face.
  • the burner gases then pass in the direction of arrow 48 into the interior between the inner coil 13 and the outer coil 14, are deflected in the space 49 in the direction of the arrow 50 and then leave the chimney 51 upward in this direction of the arrow.
  • a disk 53 is provided, which is riveted to a flange 54, which flange 54 is not fastened to the heat exchanger, but to the burner jacket 36.
  • This disk serves to reduce the flow cross section in chimney 51 in order to ensure optimal flow to ensure the burner gases.
  • the protective jacket 1 is axially centered on the chimney 51 and on the condensate drain 46. It is therefore wrapped around the burner jacket and riveted on the underside, that is, it is a winding tube which is then closed at a certain point over its entire axial length by riveting.
  • a segment 55 is also welded on in order to prevent any condensate that may form on the inside of the burner tube 36 from flowing toward the seal 38.
  • An essential feature of the present invention is therefore that the impact pot, which previously brought increased exhaust gas temperatures, is removed, which is disadvantageous.
  • the exhaust gas temperatures are now reduced because the spiral disc 18 is directly switched on in the liquid flow of the heat exchanger and is hit directly by the burner flame 47 or the burner gases.
  • the burner efficiency is now significantly increased because the exhaust gas temperature has just been reduced.
  • the exhaust gas losses must be 10% and less, which is easily achieved with the heat exchanger according to the invention.
  • the tubular heat exchanger is otherwise very easy to clean, because in addition to the provided cleaning openings 6 and 9, the tube heat exchanger can be dismantled very easily in the manner described and can therefore be cleaned thoroughly.
  • the coils 13, 14 only have to be centered on the opposite side and here pins 56 are provided which are on a Sheet 57 are welded, in this case the sheet 57 is welded to the outer circumference of the inner tube coil 13 and carries a pin 56 which bears against the inner circumference of the outer tube coil 14. There is only a touch binding there.
  • Parts 56, 57 are in turn evenly distributed at a distance of 120 ° around the circumference, it being important that the pin 56 is designed as a wearing part, so that there is no chafing point on the outer tube coil in the case of different elongations.
  • this part 56, 57 is arranged at a circumference of 120 °, so that there is no such connection in the lower part of the heat exchanger and is therefore not at risk of corrosion.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Instantaneous Water Boilers, Portable Hot-Water Supply Apparatuses, And Control Of Portable Hot-Water Supply Apparatuses (AREA)
EP92100345A 1991-01-26 1992-01-10 Wärmetauscher zur Warmwassererzeugung mit Öl- oder Gasbrennern Expired - Lifetime EP0497113B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4102314A DE4102314A1 (de) 1991-01-26 1991-01-26 Waermetauscher zur warmwassererzeugung mit oel- oder gasbrennern
DE4102314 1991-01-26

Publications (2)

Publication Number Publication Date
EP0497113A1 EP0497113A1 (de) 1992-08-05
EP0497113B1 true EP0497113B1 (de) 1994-06-01

Family

ID=6423772

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92100345A Expired - Lifetime EP0497113B1 (de) 1991-01-26 1992-01-10 Wärmetauscher zur Warmwassererzeugung mit Öl- oder Gasbrennern

Country Status (5)

Country Link
EP (1) EP0497113B1 (es)
AT (1) ATE106535T1 (es)
DE (2) DE4102314A1 (es)
DK (1) DK0497113T3 (es)
ES (1) ES2055619T3 (es)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4201687A1 (de) * 1992-01-23 1993-08-05 Wap Reinigungssysteme Waermetauscher
AT402667B (de) * 1995-03-20 1997-07-25 Vaillant Gmbh Wasserheizer wasserheizer
DE29812232U1 (de) * 1998-07-09 1999-09-09 Wap Reinigungssysteme Gmbh & Co, 89287 Bellenberg Stehender Wärmetauscher
DE102009049449A1 (de) * 2009-10-14 2011-05-26 Viessmann Werke Gmbh & Co Kg Heizkessel
DE102013109167A1 (de) * 2013-08-23 2015-02-26 Benteler Automobiltechnik Gmbh Verdampfer mit Umkehrbrennkammer
USD915012S1 (en) 2018-12-05 2021-03-30 Karcher North America, Inc. Pressure washer
US11346579B2 (en) 2019-04-24 2022-05-31 Karcher North America, Inc. Vented cover plate

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE505716C (de) * 1930-08-23 Willy Ruehl Fluessigkeitserhitzer
DE1956940U (de) * 1963-09-13 1967-03-16 Todoroff K G Dr Zwangsumlaufkessel.
DE1907987A1 (de) * 1969-02-18 1970-09-03 Wagner Geb Zwangsdurchlauferhitzer fuer aus organischen Fluessigkeiten bestehende Waermetraeger
DE6922082U (de) * 1969-06-02 1971-05-13 Standard Thermotechnik Ges Fue Zwangdurchlauf-waermeaustauscher fuer fluessige oder gasfoermige waermetraeger, insbesondere thermooel.
FR2191080B3 (es) * 1972-06-28 1976-05-21 Wanson Constr Mat Therm
US4357910A (en) * 1980-11-28 1982-11-09 Blockley Eugene T Multi-pass helical coil thermal fluid heater
DE3617556A1 (de) * 1986-05-24 1987-12-03 Friedrich Epple Gmbh & Co Hoch Hochdruck-reinigungsgeraet

Also Published As

Publication number Publication date
ATE106535T1 (de) 1994-06-15
ES2055619T3 (es) 1994-08-16
EP0497113A1 (de) 1992-08-05
DE59200184D1 (de) 1994-07-07
DK0497113T3 (da) 1994-09-26
DE4102314A1 (de) 1992-08-06

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