EP2504632B1 - Double tubing condensation exchanger for heating water and/or for producing sanitary hot water - Google Patents

Double tubing condensation exchanger for heating water and/or for producing sanitary hot water Download PDF

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Publication number
EP2504632B1
EP2504632B1 EP10790690.1A EP10790690A EP2504632B1 EP 2504632 B1 EP2504632 B1 EP 2504632B1 EP 10790690 A EP10790690 A EP 10790690A EP 2504632 B1 EP2504632 B1 EP 2504632B1
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EP
European Patent Office
Prior art keywords
coil
fumes
tubing
exchanger
plain
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
EP10790690.1A
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German (de)
French (fr)
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EP2504632A2 (en
Inventor
Marco De Nardis
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.)
Fontecal SpA
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Fontecal SpA
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Publication date
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Priority to PL10790690T priority Critical patent/PL2504632T3/en
Publication of EP2504632A2 publication Critical patent/EP2504632A2/en
Application granted granted Critical
Publication of EP2504632B1 publication Critical patent/EP2504632B1/en
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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
    • 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
    • F24H1/48—Water heaters for central heating incorporating heaters for domestic water
    • F24H1/52—Water heaters for central heating incorporating heaters for domestic water incorporating heat exchangers for domestic water
    • 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
    • F24H1/48—Water heaters for central heating incorporating heaters for domestic water
    • F24H1/52—Water heaters for central heating incorporating heaters for domestic water incorporating heat exchangers for domestic water
    • F24H1/523—Heat exchangers for sanitary water directly heated by the burner
    • 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
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
    • F28F2250/10—Particular pattern of flow of the heat exchange media
    • F28F2250/102—Particular pattern of flow of the heat exchange media with change of flow direction

Definitions

  • the present invention relates to a double tubing condensation exchanger for heating water and/or for producing sanitary hot water.
  • the invention relates to a fumes-liquid heat exchanger, permitting obtaining very high energetic efficiency with low specific load loss both on the fumes side and on the liquid side.
  • heat exchangers comprised of plain profile serpentine (without corrugation) is that they cause deposition of liquid due to condensation of combustion products within exchange interspaces for fumes.
  • the Applicant has realised a condensation heat exchanger that can solve the above problem.
  • FR 2494829 A3 describes a double tubing condensation exchanger according to the pre-characterizing portion of claim 1 of the present application.
  • said first coil is arranged inside said second coil.
  • said first coil has a cross section shape so as to conform to the profile of said second coil, particularly a pseudo-pentagonal cross section, or a rectangular cross section shape, or an ovoidal cross section shape.
  • said exchanger is a vertical fume flow exchanger or a horizontal fume flow exchanger.
  • said first and second coils are sized so a to make the relevant thermal carrier fluid reaching substantially the same temperature at the outlet of the exchanger.
  • first figures 1 and 2 it is shown a first embodiment of the heat exchanger according to the invention, generically indicated by reference number 1, according to an arrangement with a mainly vertical flow of products from combustion within the same exchanger 1.
  • Exchanger 1 provides two coiled tubings, respectively a plain tubing 2 and a corrugated tubing 3, concentrically arranged.
  • heat exchanger 1 provides that cold thermal carrier fluid, to be heated, enters within heat exchanger from below, running hydraulically parallel with respect to the two coiled tubings 2, 3 upward.
  • the two tubings 2, 3 have different profiles, and particularly, the inner one 2 being comprised of a plain tubing, with profile shown in figure 4 (or one of the different arrangements shown in figures 5 and 6 ) suitable to be coupled with corrugated tubing 3, so as to realise an optimum thermal exchange, while the outer one 3 is comprised of a flexible corrugated tubing wound as a coil.
  • the two tubings 2, 3 are adjacent to each other, and their profiles couple so as to realise an optimum exchange surface to transfer heat from combustion products to the thermal carrier fluid.
  • combustion fumes arriving from burner 4 go upward (arrows F).
  • Fumes once reached upper bottom 5, are forced to invert their direction, again going down toward lower bottom (not shown) through passages realised between corrugated tubing 3 and plain tubing 2.
  • a direct passage does not exist in this first embodiment between interstices of plain coiled tubing 2 (horizontal passages between spire of plain coil), but all fumes are forced upward and to pass within paths indicated in figure 2 .
  • heat exchanger 1 in a second embodiment providing a horizontal fumes flow.
  • cold thermal carrier fluid to be heated enters within heat exchanger from below (WATER INLET) following a hydraulically parallel path of the two coiled tubings 2, 3 upward.
  • Two coiled tubings 2 have different profiles, and particularly the inner one 2 is comprised of a plain tubing, with profile shown specifically in figure 4 , suitable to be coupled with corrugated tubing so as to realise an optimum heat exchange, while the outer one 3 is comprised of a coiled flexible corrugated tubing.
  • Said coiled tubings 2, 3 are adjacent to each other, and are realised with profiles coupled so as to realise an optimum exchange surface for transferring heat from combustion product to thermal carrier fluid.
  • Both coiled tubings 2, 3 are continuous and have no branches all along heat exchanger length 1, being connected at the bottom with return manifold and above to the inlet manifold (not shown).
  • Thermal exchange mode between gas burner 4, at the top of the combustion chamber, and the two tubings 2, 3, containing thermal carrier fluid, can be so summarised:
  • Plain coiled tubing 2 shown in figures 3 and 4 has a "pseudo-pentagonal" profile, but, as shown in figures 5 and 6 , it can be realised with different profiles (pseudo-rectangular profile, pseudo- ovoidal profile, ecc.).
  • Main function of plain tubing is that of lowering temperature of fumes arriving from combustion process (variable as a function of the kind of comburent employed and of air excess employed) up to a value of about 300°C-400°C, heating thermal carrier fluid circulating within "plain" hydraulic circuit.
  • Specific "pseudo-pentagonal" shape of plain tubing 2 of figure 4 permits an optimum coupling with corrugated tubing 3, obliging warm fumes to lick exchange surfaces of both tubings, so as to obtain maximum fumes/water heat transfer.
  • Combination of plain and corrugated tubings permits obtaining a higher efficiency.
  • System based on new coaxial combination of two coils with a different geometry, respectively comprised of a coil winding of a corrugated tubing 3, and the other one comprised of a coil winding of a plain tubing 2 (with an pseudo-pentagonal, - rectangular or - ovoidal shape, and like) permits an optimum exploitation of heat generated by hydrocarbon combustion.
  • particular fumes path permits an optimum fumes/water exchange, with useful efficiencies higher than those obtained with known solutions.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Steam Or Hot-Water Central Heating Systems (AREA)
  • Instantaneous Water Boilers, Portable Hot-Water Supply Apparatuses, And Control Of Portable Hot-Water Supply Apparatuses (AREA)

Description

  • The present invention relates to a double tubing condensation exchanger for heating water and/or for producing sanitary hot water.
  • More specifically, the invention relates to a fumes-liquid heat exchanger, permitting obtaining very high energetic efficiency with low specific load loss both on the fumes side and on the liquid side.
  • Many solutions are available on the market for condensation heat exchangers providing a single coil.
  • One drawback of heat exchangers comprised of plain profile serpentine (without corrugation) is that they cause deposition of liquid due to condensation of combustion products within exchange interspaces for fumes.
  • Known condensation heat exchangers, with a plain surface serpentine, are limited by this problem to specific boilen arrangements.
  • In view of the above, the Applicant has realised a condensation heat exchanger that can solve the above problem.
  • The problem is solved by the features as defined in claim 1.
  • FR 2494829 A3 describes a double tubing condensation exchanger according to the pre-characterizing portion of claim 1 of the present application.
  • Particularly, according to an embodiment of the invention, said first coil is arranged inside said second coil.
  • According to an embodiment of the invention, said first coil has a cross section shape so as to conform to the profile of said second coil, particularly a pseudo-pentagonal cross section, or a rectangular cross section shape, or an ovoidal cross section shape.
  • According to an embodiment of the invention, said exchanger is a vertical fume flow exchanger or a horizontal fume flow exchanger.
  • Furthermore, according to an embodiment of the invention, said first and second coils are sized so a to make the relevant thermal carrier fluid reaching substantially the same temperature at the outlet of the exchanger.
  • Embodiments of the present invention will be now described for illustrative but not limitative purposes, with reference to the figures of the enclosed drawings, wherein:
    • figure 1 schematically shows a first embodiment of the heat exchanger according to the invention;
    • figure 2 shows a particular of the heat exchanger of figure 1;
    • figure 3 schematically shows a second embodiment of the heat exchanger according to the invention;
    • figure 4 shows a first executive modification of a first particular of heat exchanger of figure 3;
    • figure 5 shows a second executive modification of a first particular of heat exchanger of figure 3; and
    • figure 6 shows a third executive modification of a first particular of heat exchanger of figure 3.
  • Observing first figures 1 and 2, it is shown a first embodiment of the heat exchanger according to the invention, generically indicated by reference number 1, according to an arrangement with a mainly vertical flow of products from combustion within the same exchanger 1.
  • Exchanger 1 provides two coiled tubings, respectively a plain tubing 2 and a corrugated tubing 3, concentrically arranged.
  • In embodiment shown in figures 1 and 2, heat exchanger 1 provides that cold thermal carrier fluid, to be heated, enters within heat exchanger from below, running hydraulically parallel with respect to the two coiled tubings 2, 3 upward.
  • The two tubings 2, 3 have different profiles, and particularly, the inner one 2 being comprised of a plain tubing, with profile shown in figure 4 (or one of the different arrangements shown in figures 5 and 6) suitable to be coupled with corrugated tubing 3, so as to realise an optimum thermal exchange, while the outer one 3 is comprised of a flexible corrugated tubing wound as a coil.
  • The two tubings 2, 3 are adjacent to each other, and their profiles couple so as to realise an optimum exchange surface to transfer heat from combustion products to the thermal carrier fluid.
  • In the first embodiment shown in figures 1 and 2, combustion fumes arriving from burner 4, go upward (arrows F).
  • Fumes, once reached upper bottom 5, are forced to invert their direction, again going down toward lower bottom (not shown) through passages realised between corrugated tubing 3 and plain tubing 2.
  • Now, hot gaseous fluids lick both corrugated tubing 3 surface and plain tubing 2 surface, both with thermal carrier liquid to be heated. Coupling of the two thus overlapped surfaces is particularly efficient for heat treatment and it is optimum as far as material use (cost/advantages ratio) is concerned. Fumes, during the path, are cooled by system water up to reaching dew temperature and thus releasing condensation latent heat (which is proportional to the amount of condensate produced). Condensates, in this first arrangement of the heat exchanger, go down vertically toward lower bottom along with fumes, with a flow always according to the same direction of the fumes flow.
  • A direct passage does not exist in this first embodiment between interstices of plain coiled tubing 2 (horizontal passages between spire of plain coil), but all fumes are forced upward and to pass within paths indicated in figure 2.
  • Referring now specifically to figure 3 of the enclosed drawings, it is shown operation of heat exchanger 1 according to the invention in a second embodiment providing a horizontal fumes flow. Here, cold thermal carrier fluid to be heated enters within heat exchanger from below (WATER INLET) following a hydraulically parallel path of the two coiled tubings 2, 3 upward.
  • Two coiled tubings 2 have different profiles, and particularly the inner one 2 is comprised of a plain tubing, with profile shown specifically in figure 4, suitable to be coupled with corrugated tubing so as to realise an optimum heat exchange, while the outer one 3 is comprised of a coiled flexible corrugated tubing.
  • Said coiled tubings 2, 3 are adjacent to each other, and are realised with profiles coupled so as to realise an optimum exchange surface for transferring heat from combustion product to thermal carrier fluid.
  • Both coiled tubings 2, 3 are continuous and have no branches all along heat exchanger length 1, being connected at the bottom with return manifold and above to the inlet manifold (not shown).
  • Thermal exchange mode between gas burner 4, at the top of the combustion chamber, and the two tubings 2, 3, containing thermal carrier fluid, can be so summarised:
    • heat exchange mainly by irradiation with inner surface of plain tubing 2 exposed toward the same burner 4;
    • convection thermal exchange, with surfaces of plain tubing interested by passage of fumes (combustion products) between inside and outside combustion chamber according to arrow A of figure 3 and fume paths of figure 4. Fumes passages are schematically indicated by parallel arrows A in figure 3 and by lines B of particular shown in figure 4;
    • by convection, with surfaces of corrugated tubing 3, lick by fumes flow both in the lower portion and in upper portion, so that tubing is fully hit by thermal flow. Particularly, the latter passage permits lowering fumes temperature under dew point of outlet fumes, thus recovering a large portion of condensation latent heat.
  • Plain coiled tubing 2 shown in figures 3 and 4 has a "pseudo-pentagonal" profile, but, as shown in figures 5 and 6, it can be realised with different profiles (pseudo-rectangular profile, pseudo- ovoidal profile, ecc.).
  • Main function of plain tubing is that of lowering temperature of fumes arriving from combustion process (variable as a function of the kind of comburent employed and of air excess employed) up to a value of about 300°C-400°C, heating thermal carrier fluid circulating within "plain" hydraulic circuit. Specific "pseudo-pentagonal" shape of plain tubing 2 of figure 4 permits an optimum coupling with corrugated tubing 3, obliging warm fumes to lick exchange surfaces of both tubings, so as to obtain maximum fumes/water heat transfer.
  • Different geometry of two tubings 2, 3 further permits realising gas/liquid heat exchange in different phases:
    • low specific surface of tubing 2 (plain tube), where fumes exchange heat at high temperature;
    • high specific surface of tubing 3, where fumes exchange heat at low temperature and mainly where it occurs condensation of fumes with contemporaneous presence of gaseous and liquid phase. Particularly, corrugated tubing 3 during this phase permits an optimum outflow of condense.
  • In other words, it is used a plain profile surface to exchange heat with fumes at a higher temperature and a corrugated surface to exchange heat with pseudo cooled and suture fumes, with presence of the beginning of formation of liquid. In the above heat exchanger 1, convective heat exchange surfaces of plain tubing 2 (interspaces between coils) have been studied to prevent at most formation of condensate inside, in order to prevent that deposition of liquid in these passages hinders regular path of fumes during some heat exchanger operation modes.
  • By the solution suggested according to the present invention, many advantages are obtained with respect to the known solutions.
  • Particularly, advantages are obtained both in terms of efficiency and in term of functionality and reliability.
  • Combination of plain and corrugated tubings permits obtaining a higher efficiency. System based on new coaxial combination of two coils with a different geometry, respectively comprised of a coil winding of a corrugated tubing 3, and the other one comprised of a coil winding of a plain tubing 2 (with an pseudo-pentagonal, - rectangular or - ovoidal shape, and like) permits an optimum exploitation of heat generated by hydrocarbon combustion. In fact, particular fumes path permits an optimum fumes/water exchange, with useful efficiencies higher than those obtained with known solutions.
  • It is further obtained a lower hydraulic load loss with respect to a system with a single coil, since, with respect to solutions with a single coil known, the system suggested according to the invention permits a lower hydraulic load loss of thermal carrier fluid. In fact, a hydraulic parallel path comprised of the two coils and their particular geometry permits remarkably reducing divided and concentrated load loss of heat exchanger with respect to a single coil exchanger with the same exchange surface.
  • Finally, it is realised an optimum condensate evacuation system, due to original and new heat exchange system and to the specific "plain/corrugated" architecture permitting, with respect to the mainly employed solutions, a higher flexibility when positioning the heat exchanger within the thermal generator.
  • Particular geometry of the suggested heat exchanger makes it possible that condensate only forms close to the corrugated outer coil and not close to interspaces of plain tubing, thus preventing all problems connected to presence of liquid between said interspaces of plain tubing.
  • Present invention has been described for illustrative, but not limitative, purposes, according to its preferred embodiments, but it is to be understood that variations and/or modifications can be introduced by those skilled in the art without departing from the scope as defined in the enclosed claims.

Claims (3)

  1. Double tubing condensation exchanger for heating water and/or for producing sanitary hot water, providing a first coil (2) with a plain surface and a second coil (3) with a corrugated surface, provided in parallel to each other, said first and second coils being spiral wound, a thermal carrier fluid can circulate, independently, inside said first and second coils, said first coil can exchange heat with combustion fumes mainly by irradiation and convection, said exchanger being characterized in that said second coil is arranged such that it can exchange heat with combustion fumes mainly by condensation.
  2. Double tubing condensation exchanger according to claim 1, characterised in that said first coil is arranged inside said second coil.
  3. Double tubing condensation exchanger according to one of the preceding claims, characterised in that said first coil has a cross section shape so as to conform to the profile of said second coil, particularly a pseudo-pentagonal cross section, or a rectangular cross section shape, or an ovoidal cross section shape.
EP10790690.1A 2009-11-24 2010-11-17 Double tubing condensation exchanger for heating water and/or for producing sanitary hot water Active EP2504632B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL10790690T PL2504632T3 (en) 2009-11-24 2010-11-17 Double tubing condensation exchanger for heating water and/or for producing sanitary hot water

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
ITRM2009A000614A IT1396729B1 (en) 2009-11-24 2009-11-24 CONDENSER HEAT EXCHANGER WITH DOUBLE PIPING FOR HEATING WATER AND / OR PRODUCTION OF DOMESTIC HOT WATER.
PCT/IT2010/000459 WO2011064804A2 (en) 2009-11-24 2010-11-17 Double tubing condensation exchanger for heating water and/or for producing sanitary hot water

Publications (2)

Publication Number Publication Date
EP2504632A2 EP2504632A2 (en) 2012-10-03
EP2504632B1 true EP2504632B1 (en) 2015-03-04

Family

ID=42315635

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10790690.1A Active EP2504632B1 (en) 2009-11-24 2010-11-17 Double tubing condensation exchanger for heating water and/or for producing sanitary hot water

Country Status (7)

Country Link
EP (1) EP2504632B1 (en)
CN (1) CN102713453B (en)
ES (1) ES2538392T3 (en)
HK (1) HK1176394A1 (en)
IT (2) IT1396729B1 (en)
PL (1) PL2504632T3 (en)
WO (1) WO2011064804A2 (en)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT202200013435A1 (en) 2022-06-27 2023-12-27 Riello Spa HEAT EXCHANGER FOR BOILER, IN PARTICULAR FOR CONDENSING BOILER, AND BOILER INCLUDING SAID EXCHANGER

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103940087B (en) * 2014-04-09 2017-04-05 西安交通大学 A kind of narrow gap oblateness dual coil pipes entirety condensing boiler
US10024603B2 (en) * 2014-11-26 2018-07-17 Riello S.P.A. Double tubing condensation exchanger for heating water and/or for producing sanitary hot water
WO2016207923A1 (en) * 2015-06-24 2016-12-29 Fontecal S.P.A. Profile of piping for a heat exchanger, heat exchanger for condensation boilers providing said profile, and condensation boiler providing said heat exchanger
IT201700081975A1 (en) * 2017-07-19 2019-01-19 Calini Donatella AN ENERGY PRODUCTION SYSTEM FOR EXTERNAL COMBUSTION TURBINES

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2494829A3 (en) * 1980-11-21 1982-05-28 Ciat Sa Coaxial fluid heat exchanger - has container with helicoidally waved pipes for liquid flowing in opposing directions
US7428883B2 (en) * 2004-05-11 2008-09-30 Noritz Corporation Heat exchanger and water heater

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT202200013435A1 (en) 2022-06-27 2023-12-27 Riello Spa HEAT EXCHANGER FOR BOILER, IN PARTICULAR FOR CONDENSING BOILER, AND BOILER INCLUDING SAID EXCHANGER
WO2024003957A1 (en) * 2022-06-27 2024-01-04 Riello S.P.A. Boiler, in particular a condensing boiler, comprising a heat exchanger

Also Published As

Publication number Publication date
ES2538392T3 (en) 2015-06-19
WO2011064804A2 (en) 2011-06-03
ITRM20100599A1 (en) 2011-05-25
PL2504632T3 (en) 2015-10-30
WO2011064804A3 (en) 2012-05-10
IT1403750B1 (en) 2013-10-31
HK1176394A1 (en) 2013-07-26
EP2504632A2 (en) 2012-10-03
ITRM20090614A1 (en) 2011-05-25
IT1396729B1 (en) 2012-12-14
CN102713453A (en) 2012-10-03
CN102713453B (en) 2015-05-27

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