EP1703227A2 - Echangeur de chaleur - Google Patents

Echangeur de chaleur Download PDF

Info

Publication number
EP1703227A2
EP1703227A2 EP06004561A EP06004561A EP1703227A2 EP 1703227 A2 EP1703227 A2 EP 1703227A2 EP 06004561 A EP06004561 A EP 06004561A EP 06004561 A EP06004561 A EP 06004561A EP 1703227 A2 EP1703227 A2 EP 1703227A2
Authority
EP
European Patent Office
Prior art keywords
heat exchanger
coil
exchanger according
helix
helices
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP06004561A
Other languages
German (de)
English (en)
Other versions
EP1703227B1 (fr
EP1703227A3 (fr
Inventor
Lila Menari
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.)
Vaillant GmbH
Original Assignee
Vaillant GmbH
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 Vaillant GmbH filed Critical Vaillant GmbH
Publication of EP1703227A2 publication Critical patent/EP1703227A2/fr
Publication of EP1703227A3 publication Critical patent/EP1703227A3/fr
Application granted granted Critical
Publication of EP1703227B1 publication Critical patent/EP1703227B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/02—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled
    • F28D7/024—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being helically coiled the conduits of only one medium being helically coiled tubes, the coils having a cylindrical configuration
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • F28F9/0132—Auxiliary supports for elements for tubes or tube-assemblies formed by slats, tie-rods, articulated or expandable rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2210/00—Heat exchange conduits
    • F28F2210/04—Arrangements of conduits common to different heat exchange sections, the conduits having channels for different circuits

Definitions

  • the present invention relates to devices for heating liquids, such as boilers and water heaters, and more particularly to the heat exchangers of such devices.
  • the said devices contain a heat source, usually in the form of a gas burner, the hot exhaust gases are passed to a gas-liquid heat exchanger, which often consists of a helically wound tube through which flows the liquid to be heated.
  • a heat source usually in the form of a gas burner
  • the hot exhaust gases are passed to a gas-liquid heat exchanger, which often consists of a helically wound tube through which flows the liquid to be heated.
  • the hot exhaust gases are, after they have flowed around the pipe and thereby released thermal energy, released into the atmosphere.
  • the thermal efficiency depends on the quality of the energy transfer between exhaust and heat exchanger tube. This transmission is mainly determined by the contact time between the exhaust gas and the pipe and by the turbulence of the flow of the hot exhaust gases. Therefore, it is necessary to extend the area where the hot exhaust gases and the pipe come into contact.
  • the helical tubes are oval in cross-section and are kept by means of incorporated web-shaped spacers to size.
  • the heat exchanger has only one stage or coil for the exchange of thermal energy.
  • the aim of the present invention is to increase the efficiency of heat exchange between hot, from a heat source such as a burner, originating gases and the flowed through by a fluid to be heated coils of a heat exchanger by means of a suitable arrangement.
  • the invention first relates to a heat exchanger for the thermal coupling of hot, derived from a burner exhaust gases with a tube through which flows a liquid to be heated.
  • the tube is wound helically around the burner. Due to the generous gaps between the windings, the exhaust gases produced during the combustion process can be transformed into one Exhaust duct of a heat exchanger shell, which encloses the tube, are discharged radially.
  • the heat exchanger contains at least two coils, which are arranged mutually coaxial and generally radially overlapping, wherein the two coils have the same coil spacing and the axial offset to each other is almost half a helix distance.
  • the two serially or parallelly arranged spirals form two concentric walls which enclose the space in which hot exhaust gases are formed and allow them to escape radially through the gaps of their windings. Due to the offset by half a helix distance, the centers of the circular cross-sectionally or axially flattened turns of both helices are arranged in an axial plane, like the tips of an isosceles triangle. For this reason, the exhaust gases first flow through the gaps of two adjacent turns of the inner coil and then impinge on the turn of the outer coil virtually at the apex of the isosceles triangle.
  • the exhaust stream is split into two nearly identical sub-streams, which flow over both sides of the turns of the outer helix, before they exit radially through the gaps of the outer helix.
  • the outer turns are therefore an obstacle, which increases the duration of the exhaust pipe contact and thus the effectiveness.
  • the incorporation of one or more additional coils surrounding the outer coil according to the axial displacement principle described above can further increase the yield.
  • the invention is independent of the shape of the turns.
  • the cross sections of the turns do not necessarily have to be circular.
  • the embodiment of the invention with oval, lens or diamond-shaped cross sections is also possible.
  • the outer coil is colder than the inner coil, which in addition to the hot exhaust gas is also exposed to the direct heat radiation of the burner, while the outer coil provides a large surface area for the condensation of the liquid, usually water, which has been previously evaporated in the space bounded by the inner coil.
  • the outer diameter of the inner coil is larger than the inner diameter of the outer coil. Consequently, the inner coil can not be inserted by a simple translational movement in the outer coil.
  • the turns of the built-in inner coil radially project into the interstices of the turns of the outer coil and thus define axially oblique gaps between the turns of both coils, which can be calibrated on the basis of the purely axial gaps between the turns of a coil. It therefore gives the impression as if the turns of both coils are firmly intermeshed.
  • the exhaust gases initially flow through the gaps of the inner coil and pass through an oblique, located between the two coils, gap in the gaps of the outer coil. If the gaps between the turns and between the helices are the same size, the exhaust gases experience an almost constant pressure loss during the flow through the helices.
  • a plate axially divides the interior of the inner coil into a first region in which the burner is placed and a second, axially remote region in which the exhaust port is located.
  • the exhaust gases exit radially from the burner region, then follow an axial path into a layer-like region lying between the outside of the outer coil and the inside of the heat exchanger shell, and finally flow along a radial path into the second region before they pass flow out through the exhaust port.
  • the deflection path obtained by the baffle plate which ensures a double heat exchange.
  • an axially aligned comb has brackets for supporting the inner coil.
  • the comb is disposed between the inner and outer coils and keeps the gaps between the turns of the inner coil at the desired distance.
  • the comb therefore forms a template which limits a thermally induced axial deformation of the inner coil.
  • the comb may also have brackets for the outer coil, whereby it can be arranged with respect to the inner coil with an axial offset of half a helix distance and a desired radial distance.
  • the comb can also be mounted on the radially outer side of the outer coil to define these supports and their distances.
  • a torque may be exerted on the inner coil, so that its outer diameter decreases.
  • clips or brackets can be attached, which maintain the torque during assembly.
  • a torque is applied to the outer coil to increase its inner diameter.
  • the outer coil is relieved after said translation of the inner coil again.
  • Object of the present invention is to increase the efficiency of heat exchange in heaters, especially gas-fired condensing appliances by a suitable heat exchanger, which is inexpensive and is characterized by a simple manufacturing process.
  • FIG. 1 shows a schematic diagram of the heat exchanger according to the invention in cross-section.
  • the heat exchanger is delimited by a housing 1 whose lateral wall 1C is cylindrical, has a predetermined axial length and is preferably radially symmetrical to a vertical central axis 9, wherein axially opposite water supply lines 5 and Water outlet pipes 6 with two above and below also opposite sealing walls 1A, 1B, in the present embodiment, there are plates connected.
  • a burner 3 is arranged, which flows in the heat exchanger tubes Heated water.
  • the tubes are preferably made of stainless steel and processed into spirals with spiral turns.
  • the heat exchanger according to the invention contains at least two such coils 20, 30, which are arranged coaxially and overlap radially.
  • the helix diameters have the values D1 and D2, whereby D2 is greater than D1.
  • the axial length of the coils 20, 30 is almost equal and corresponds to the length of the housing 1.
  • the helix spacing preferably has the same value P for both helices 20, 30. Due to an axial offset of the helices 20 and 30 by P / 2, a radial plane X - X contacts both the center of an inner helical turn and the center of the opposite outer helical turn ,
  • the inner coil 20 includes an approximately cylindrical volume, which is divided by a deflecting plate 19 axially into two sub-volumes.
  • This deflecting plate 19 is arranged in a radial plane, preferably axially in the center of the housing 1, and defines a first inner upper volume 10, in which the burner 3 is located, and a second inner lower volume 15, which is connected to an exhaust pipe 4, from each other.
  • the turns of the inner coil 20 are held by U-shaped brackets 23 and the turns of the outer coil 30 via a comb-like holder 33 at a defined distance.
  • the heat exchanger according to the invention is incorporated in a heating circuit in which a pump 50 via the water supply lines 5 to the water inlets 21 and 31 of the two Spirals 20, 30 is connected. In the upper part of the water outlets 22 and 32 are connected to the water outlet 6, which in turn to a consumer device, such as a radiator 7, are connected.
  • the hydraulic heating circuit to the pump 50 is closed via a feedback with a return line 8.
  • the disclosure of the invention which relates to the structure and operation of the device, is made for an operating position in which the axis of the device is arranged vertically.
  • the present disclosure also applies to a different axis alignment with the corresponding conversions of the respective components.
  • the burner 3 is supplied via a gas line 2 from an external gas source 40.
  • an exhaust pipe 4 via which the cooled off at the heat exchanger tubes exhaust gases are removed.
  • the gas stream is preferably assisted by a fan, which is not shown.
  • the helices 20 and 30 are connected in parallel.
  • the two coils 20, 30 are flowed through in the same direction by the liquid to be heated. Consequently, the inner 20 and outer 30 coils are fed via their respective water inlet 21, 31 through the corresponding water supply line 5.
  • the liquid passes in the inner 20 and the outer coil 30 first a colder 15, then a warmer 10 area and thus undergoes gradual heating, the inner coil 20 in the lower region 15 initially colder, in the upper region 10th but warmer water leads than the outer coil 30.
  • the exhaust gases give off part of their thermal energy during heat exchange in the upper region 10, before they reach the lower region 15. Since in the latter area 15 cold liquid is fed and a temperature gradient from the exhaust gas to the liquid exists, takes place in this area 15, a heat exchange.
  • the coils 20, 30 may be connected in series. In a serial operation, the two coils 20, 30 are flowed through in opposite directions by the liquid to be heated. In this case, the coupling of the helices 20, 30 can be done in two ways.
  • the return can take place via the water inlet 21 of the inner coil 20.
  • the cold liquid hits in the lower area 15 on the coldest exhaust gases. Due to the heat exchange that takes place, thermal energy is withdrawn from the cold exhaust gases, which leads to an increased formation of condensate in this section.
  • the liquid enters the warmest area 10, in which, in addition to the hottest exhaust gases and the direct heat radiation of the burner 3 heats the water.
  • the water is passed through the two upper connected water outlets 22, 32 in the outer coil 30, where it is further heated and finally exits as a flow from the water inlet 31.
  • a disadvantage of this constellation is the relatively low energy yield due to the rather short preheating of the inner coil 20 in the lower region 15th
  • the return can take place in the second case via the lower end 31 of the outer coil 30.
  • the cold liquid hits the already cooled exhaust gases in the lower region 15 and is preheated.
  • a further preheating in the upper region 10 takes place based on the hotter exhaust gases located there.
  • the water passes over the upper interconnected water outlets 22, 32 in the inner coil 20 and is in the warmest region 10, in which, in addition to the hottest exhaust gases and the direct heat radiation of the burner 3 strikes the turns of the inner coil 20, heated.
  • no or hardly any heat energy is withdrawn from the coldest exhaust gases, since the water present in the inner coil 20 is substantially warmer than the exhaust gases present in this section, which leads to a reduction of the yield in this region 15. Condensation is relatively small in this arrangement.
  • the water inlet 21 of the inner coil 20 the water finally exits as a flow. Due to the extended preheat range, which extends over virtually the entire length of the outer coil 30, the thermal energy yield can be increased.
  • the radial arrow F0 represents the path of a flow of hot exhaust gases leaving the burner 3, said flow F0 being directed from the central axis 9 to the outer coil 30.
  • the flux F0 passes through a first gap or a first gap E1 of calibrated height between the turns of the inner coil 20.
  • the axial height coincides with the difference resulting from the helix pitch P and a diameter value d1, which is obtained from the cross section of FIG Tube receives the inner coil 20 results.
  • the first gap E1 is in the present embodiment 0.9 mm at a pipe diameter d1 of the inner coil 20 of 14 mm and therefore at a coil pitch P of 14.9 mm, wherein the coil diameter D1 of the inner coil 20 is about 20 cm.
  • the flow F0 which leaves the inner upper volume 10 bounded by the inner coil 20 radially outward, after having been initially axially constricted, reaches a position which is at the same height as the centers C1 of the tube cross-sections of the inner coil 20 Following its radial path beyond the first gap E1, the flux F0 axially extends into an inner cylindrical space 11 defined by the coils 20 and 30.
  • the flow F0 then encounters a turn of the outer coil 30. Because of the offset by half a helix distance (P / 2) between the helices 20 and 30, the flow F0 splits into practically two equal sub-flows F1, F2 and flows over both sides of the impacted turn of the outer helix 30.
  • the sub-flows F1, F2 each pass through a further gap E2, which are bounded axially by two turns of the outer coil 30.
  • the partial flows F1 and F2 then impinge radially on the cylindrical wall of the housing 1.
  • the flows F1 and F2 then flow axially in an outer cylindrical space 12 to the ground.
  • the intermediate space 12 which is bounded by the inner surface of the cylindrical housing wall 1 and the outer coil 30, run all, corresponding to the rivers F1 and F2, Halfladore together until they reach the height of the deflecting plate 19 axially.
  • the outer cylindrical gap 12 merges into a volume 13 from which flows, as shown by arrow F10, flow radially in the direction of the central axis 9.
  • the flows pass through the gaps E2 and split in the intermediate space 14, which is analogous to the gap 11, into two practically identical partial flows F11 and F12, which flow through the corresponding gaps E1, wherein the Flow direction opposite to the direction of the rivers F1, F2 is opposite.
  • a detailed description will be omitted here.
  • the incorporation of an odd or even number of such separator plates 19 may be considered.
  • a direct connection between the cylindrical outer volume 13 and the exhaust pipe 4 can be made by the lower turns of the coils 20, 30 are omitted at the level of the water inlets 21 and 31.
  • the coil pitch P can be determined.
  • the tube diameter d2 of the outer coil 30 may be smaller than, equal to or larger than the diameter value d1 of the inner coil 20.
  • the second gap E2 may or may not have a value identical to that of the first gap E1.
  • a difference value for the average curvature radii R1 and R2 may be selected from a predefined range. The choice of the dimensions determines a composite gap E3, that is, a gap that reflects the oblique spacing between the two coils 20, 30.
  • An inner spacer has the shape of a U-shaped bracket 23, which is fastened to the tubes of the inner coil 20 like a clip.
  • the U-shaped extends Clamp 23 preferably to the center of the pipe C1, to ensure better adhesion to the pipe sections.
  • the diameter of the wire from which the clip 23 was made defines the gap E1.
  • the U-shaped bracket 23 is advantageously mounted between the outer 30 and the inner 20 coil, so that in addition to the columns E1 additionally the oblique columns E3 are defined by the wire diameter.
  • FIG. 4 shows another comb-like holder 36 located between the coils 20, 30.
  • the comb-like holder 36 has arms 34 which support the tubes of the inner coil 20.
  • the height of the arms 34 defines the axial gap E1 between two turns of the inner coil 20.
  • the comb-like support 36 preferably has a V-shape, wherein the axial distance from the V-tips to the adjacent arms 34 is a half helix pitch P / 2.
  • the holder 36 can be considered as a chain of Vs with an opening angle of 120 degrees that propagates in the axial direction to the coils 20, 30. In cross section, each three adjacent turns form an equilateral triangle.
  • the holder 36 defines over its profile and its width the oblique gap E3 between the helices 20, 30th
  • the arms 34 of the comb-like support 36 preferably extend at least to the centers C1, C2 of the helical tubes. Furthermore, by notches on the open sides of the arms 34 springs 35 can be created, which clamp the tubes between two arms 34.
  • the comb-like holder 36 is made of a rectangular piece of sheet metal. This Sheet is first provided with notches, which represent the later springs 35. Subsequently, the arms 34 are punched out, which have an angle of about 90 ° to the original sheet. In a subsequent step, the main piece is pressed into said V-shape ( Figures 4-6).
  • the comb-like holder 36 is looped through into the spaces 11, 14 located between the coils 20, 30, wherein an optional elastic deformation of the holder 36 and / or the coils 20, 30 facilitates insertion. Also, the use of the holder 36 in the region of the outer coil 30, as shown in Fig. 1, possible. A combination of the previously described U-shaped bracket 23 and the comb-like holder 36 is also conceivable. Thus, for example, the comb-like holder 36 can be introduced between the two coils 20, 30, while on the radially outer side of the outer coil 30 placed U-shaped brackets 23, the columns E2 additionally hold to measure.
  • Figures 2 and 3 show the housing 1 with the opposite walls 1 A and 1 B without the lateral wall 1C.
  • the helices 20, 30 are clamped and fixed by web-shaped spacers 41 such that there is a constant gap between the helical turns.
  • the spacers 41 have a pin-shaped structure with notches 42 in the upper and lower edge region (FIG. 7).
  • the helices 20, 30 are axially clamped over at least two walls 1A, 1B. This tension is maintained by attaching at least two web-shaped spacers 41 to the walls so that their notches engage the walls 1A, 1B thereby avoiding their discharge.
  • the length of the spacers 41 determines the distance between the axially opposite walls 1A and 1B.
  • the web-shaped spacers 41 may alternatively be used in combination with or in combination with the aforementioned devices 23 and 36.
EP20060004561 2005-03-15 2006-03-07 Echangeur de chaleur Active EP1703227B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005012235 2005-03-15

Publications (3)

Publication Number Publication Date
EP1703227A2 true EP1703227A2 (fr) 2006-09-20
EP1703227A3 EP1703227A3 (fr) 2012-05-30
EP1703227B1 EP1703227B1 (fr) 2015-02-25

Family

ID=36600180

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20060004561 Active EP1703227B1 (fr) 2005-03-15 2006-03-07 Echangeur de chaleur

Country Status (3)

Country Link
EP (1) EP1703227B1 (fr)
DK (1) DK1703227T3 (fr)
ES (1) ES2536445T3 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1965146A1 (fr) 2007-02-28 2008-09-03 Joseph Le Mer Echangeur de chaleur à condensation comprenant deux faisceaux primaires et un faisceau secondaire
EP2381186A1 (fr) * 2010-02-26 2011-10-26 Daikin Industries, Ltd. Élément de support de serpentin
DE102012006407A1 (de) 2012-03-29 2013-10-02 Vaillant Gmbh Wärmetauscher
EP2784408A1 (fr) * 2013-03-28 2014-10-01 Viessmann Werke GmbH & Co. KG Chaudière
WO2015160498A3 (fr) * 2014-04-15 2016-03-24 Ecr International, Inc. Échangeur de chaleur
IT201600074665A1 (it) * 2016-07-18 2018-01-18 Ariston Thermo Spa Scambiatore di calore per caldaia o simili

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105135678B (zh) * 2015-09-23 2018-08-07 安徽三鼎锅炉制造有限公司 有机热载体供热设备

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4981171A (en) 1988-09-13 1991-01-01 Rite Coil, Inc. Heat exchange coil
DE4428097A1 (de) 1994-08-09 1996-02-22 Bosch Gmbh Robert Verfahren zum Betreiben eines Heizgerätes sowie Heizgerät zur Durchführung des Verfahrens
EP0678186B1 (fr) 1993-01-15 1997-03-12 Joseph Le Mer Element echangeur de chaleur, procede et dispositif pour le fabriquer
DE29906481U1 (de) 1998-04-06 1999-07-29 Vaillant Joh Gmbh & Co Wasserheizer

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE605213C (de) * 1932-11-11 1934-11-07 Josef Kurz Vorrichtung zur Lagerung von Rohrleitungen, insbesondere von Rohrschlangen, in Gestalt eines Flach-, T- oder eines anderen Profileisens mit dem Querschnitt der Rohre entsprechenden Ausschnitten
FR2191089A1 (fr) * 1972-07-03 1974-02-01 Ciat Sa
US4798240A (en) * 1985-03-18 1989-01-17 Gas Research Institute Integrated space heating, air conditioning and potable water heating appliance
EP0344351A1 (fr) * 1988-06-03 1989-12-06 VIA Gesellschaft für Verfahrenstechnik mbH Gaz frigorigène-échangeur de chaleur, spécialement pour des sécheurs d'air comprimé
US4901677A (en) * 1988-12-21 1990-02-20 Gas Research Institute Finned-tube heat exchanger with liquid-cooled baffle

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4981171A (en) 1988-09-13 1991-01-01 Rite Coil, Inc. Heat exchange coil
EP0678186B1 (fr) 1993-01-15 1997-03-12 Joseph Le Mer Element echangeur de chaleur, procede et dispositif pour le fabriquer
DE4428097A1 (de) 1994-08-09 1996-02-22 Bosch Gmbh Robert Verfahren zum Betreiben eines Heizgerätes sowie Heizgerät zur Durchführung des Verfahrens
DE29906481U1 (de) 1998-04-06 1999-07-29 Vaillant Joh Gmbh & Co Wasserheizer

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1965146A1 (fr) 2007-02-28 2008-09-03 Joseph Le Mer Echangeur de chaleur à condensation comprenant deux faisceaux primaires et un faisceau secondaire
AU2010346932B8 (en) * 2010-02-26 2013-10-17 Daikin Europe N.V. Coil support member
US9702587B2 (en) 2010-02-26 2017-07-11 Daikin Industries, Ltd. Water storage vessel assembly with coil support member
CN102762930A (zh) * 2010-02-26 2012-10-31 大金工业株式会社 线圈支承构件
EP2381186A4 (fr) * 2010-02-26 2012-01-04 Daikin Ind Ltd Élément de support de serpentin
AU2010346932B2 (en) * 2010-02-26 2013-10-03 Daikin Europe N.V. Coil support member
EP2381186A1 (fr) * 2010-02-26 2011-10-26 Daikin Industries, Ltd. Élément de support de serpentin
CN102762930B (zh) * 2010-02-26 2014-12-10 大金工业株式会社 线圈支承构件
DE102012006407A1 (de) 2012-03-29 2013-10-02 Vaillant Gmbh Wärmetauscher
DE102013103191A1 (de) * 2013-03-28 2014-10-02 Viessmann Werke Gmbh & Co Kg Heizkessel
EP2784408A1 (fr) * 2013-03-28 2014-10-01 Viessmann Werke GmbH & Co. KG Chaudière
WO2015160498A3 (fr) * 2014-04-15 2016-03-24 Ecr International, Inc. Échangeur de chaleur
US10012413B2 (en) 2014-04-15 2018-07-03 Ecr International, Inc. Heat exchanger
IT201600074665A1 (it) * 2016-07-18 2018-01-18 Ariston Thermo Spa Scambiatore di calore per caldaia o simili
WO2018015799A1 (fr) * 2016-07-18 2018-01-25 Ariston Thermo S.P.A. Echangeur de chaleur pour chaudière

Also Published As

Publication number Publication date
EP1703227B1 (fr) 2015-02-25
EP1703227A3 (fr) 2012-05-30
DK1703227T3 (da) 2015-05-26
ES2536445T3 (es) 2015-05-25

Similar Documents

Publication Publication Date Title
EP0278961B1 (fr) Echangeur de chaleur a contre-courant a faisceau helicoidal de tubes
EP1703227B1 (fr) Echangeur de chaleur
WO2005088208A1 (fr) Echangeur thermique comprenant un tube a vide
DE102010008175B4 (de) Wärmeübertrager
DE60307323T4 (de) Wärmetauscher
EP2096372A2 (fr) Appareil de chauffage
CH666539A5 (de) Waermetauscherrohr und daraus gebildeter waermetauscher.
DE10348141B3 (de) Innerer Wärmeübertrager für Hochdruckkältemittel mit Akkumulator
EP2937658B1 (fr) Fluide caloporteur interne
EP2157382A2 (fr) Appareil de chauffage
DE102009041773A1 (de) Wärmetauscherrohr, Wärmetauscher und raumlufttechnische Anlage
DE102008014523A1 (de) Heizgerät
DE102006011147A1 (de) Wärmetauscher
EP0172363B1 (fr) Appareil échangeur de chaleur, en particulier pour refroidir les gaz d'un réacteur à haute température
EP3800418B1 (fr) Échangeur de chaleur, installation de réfrigération ou de chauffage doté d'un tel échangeur de chaleur
DE202017104743U1 (de) Wärmetauscher mit Mikrokanal-Struktur oder Flügelrohr-Struktur
DE202019103964U1 (de) Wärmeaustauscher
EP3367035A1 (fr) Échangeur thermique serpentin et réservoir de stockage pourvu d'un échangeur thermique serpentin
EP0026271B1 (fr) Echangeur de chaleur, en particulier pour chauffe-eau à mazout ou à gaz
DE10105202A1 (de) Wärmeübertrager-Rohrblock mit mehreren geschlitzten Sammelrohren
WO2009000669A1 (fr) Appareil réfrigérant
DE102006001351A1 (de) Spiralwärmetauscher
CH660075A5 (de) Gegenstrom-roehren-waermetauscher.
DE202023105664U1 (de) Wärmetauscher mit kontinuierlicher wendelförmiger Prallplatte
DE10341644B4 (de) Wendelförmiger Wärmeaustauscher

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

RIC1 Information provided on ipc code assigned before grant

Ipc: F28F 9/013 20060101ALI20120426BHEP

Ipc: F24H 1/43 20060101AFI20120426BHEP

Ipc: F28D 7/02 20060101ALI20120426BHEP

Ipc: F28D 7/00 20060101ALI20120426BHEP

17P Request for examination filed

Effective date: 20121119

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

17Q First examination report despatched

Effective date: 20130808

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20140821

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502006014197

Country of ref document: DE

Effective date: 20150409

REG Reference to a national code

Ref country code: AT

Ref legal event code: REF

Ref document number: 712325

Country of ref document: AT

Kind code of ref document: T

Effective date: 20150415

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2536445

Country of ref document: ES

Kind code of ref document: T3

Effective date: 20150525

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

Effective date: 20150521

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

REG Reference to a national code

Ref country code: SK

Ref legal event code: T3

Ref document number: E 18584

Country of ref document: SK

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

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150526

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150625

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

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

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502006014197

Country of ref document: DE

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

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

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

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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

Ref country code: IE

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

Effective date: 20150307

26N No opposition filed

Effective date: 20151126

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

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 11

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

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

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20060307

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

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

Ref country code: AT

Payment date: 20170215

Year of fee payment: 12

Ref country code: DK

Payment date: 20170303

Year of fee payment: 12

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

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150225

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

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20150625

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

Ref country code: LU

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

Effective date: 20150307

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

Effective date: 20180331

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 712325

Country of ref document: AT

Kind code of ref document: T

Effective date: 20180307

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

Ref country code: AT

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

Effective date: 20180307

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

Ref country code: DK

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

Effective date: 20180331

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

Ref country code: CH

Payment date: 20210303

Year of fee payment: 16

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Ref country code: LI

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

Effective date: 20220331

Ref country code: CH

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

Effective date: 20220331

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

Ref country code: NL

Payment date: 20230228

Year of fee payment: 18

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

Ref country code: FR

Payment date: 20230322

Year of fee payment: 18

Ref country code: CZ

Payment date: 20230224

Year of fee payment: 18

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

Ref country code: TR

Payment date: 20230301

Year of fee payment: 18

Ref country code: SK

Payment date: 20230223

Year of fee payment: 18

Ref country code: GB

Payment date: 20230228

Year of fee payment: 18

Ref country code: DE

Payment date: 20230228

Year of fee payment: 18

Ref country code: BE

Payment date: 20230228

Year of fee payment: 18

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

Ref country code: IT

Payment date: 20230331

Year of fee payment: 18

Ref country code: ES

Payment date: 20230403

Year of fee payment: 18