EP3076101A2 - Wärmeübertrager und anordnung eines wärmetauschers und eines brenners - Google Patents

Wärmeübertrager und anordnung eines wärmetauschers und eines brenners Download PDF

Info

Publication number
EP3076101A2
EP3076101A2 EP16159342.1A EP16159342A EP3076101A2 EP 3076101 A2 EP3076101 A2 EP 3076101A2 EP 16159342 A EP16159342 A EP 16159342A EP 3076101 A2 EP3076101 A2 EP 3076101A2
Authority
EP
European Patent Office
Prior art keywords
pipes
heat exchanger
burner
shape body
group
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.)
Pending
Application number
EP16159342.1A
Other languages
English (en)
French (fr)
Other versions
EP3076101A3 (de
Inventor
Johannes LAMMERS
Johannes Hendrikus Maria VAN DER LANS
Gerrit Willem LAMMERS
Rudi Meinen
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.)
ATAG Heating Holding BV
Original Assignee
ATAG VERWARMING NEDERLAND BV
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 ATAG VERWARMING NEDERLAND BV filed Critical ATAG VERWARMING NEDERLAND BV
Publication of EP3076101A2 publication Critical patent/EP3076101A2/de
Publication of EP3076101A3 publication Critical patent/EP3076101A3/de
Pending legal-status Critical Current

Links

Images

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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • 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
    • F28D7/0041—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 for only one medium being tubes having parts touching each other or tubes assembled in panel form
    • 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
    • F28D7/16—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 arranged in parallel spaced relation
    • F28D7/163—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 arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing
    • F28D7/1638—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 arranged in parallel spaced relation with conduit assemblies having a particular shape, e.g. square or annular; with assemblies of conduits having different geometrical features; with multiple groups of conduits connected in series or parallel and arranged inside common casing with particular pattern of flow or the heat exchange medium flowing inside the conduits assemblies, e.g. change of flow direction from one conduit assembly to another one
    • 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
    • F28F2210/08—Assemblies of conduits having different features

Definitions

  • the invention relates to a heat exchanger, comprising:
  • Such a heat exchanger is known from European patent EP-B1-0687870 in the name of the same applicant. It is an object to improve the heat exchanger described in EP-B1-0687870 .
  • said receiving space is arranged between at least a part of the pipes of the first pattern located near the open end of the U-shape body in such a manner that in use at least a part of the pipes of the first pattern surround a flame provided by said burner.
  • An advantage of this embodiment is that the casing is protected from the heat of the flame by said pipes of the first pattern that surround said flame.
  • the flame was present in an area not bounded by pipes. Practically the heat exchanger therefor had a sealing arranged to protect the casing from the heat, which sealing is quite expensive.
  • An advantage of this embodiment is therefore that no or less sealing is required, thereby reducing the costs of the heat exchanger.
  • a distance between all pairs of adjacent pipes of each leg of the first pattern is maximally 0.5 mm, preferably maximally 0.1 mm.
  • said distance is defined as the distance between the adjacent outer surfaces of each pair of adjacent pipes.
  • said heat exchanger comprises a sealing arranged between the outer surface of the pipes arranged at a first end of each leg of the first pattern near the open end of the U-shape body and the substantially U-shaped body.
  • the distance between the legs of the U-shape body and the pipes of the first pattern is maximally 1.0 mm, preferably maximally 0.4 mm.
  • said distance is defined as the distance between the outer surfaces of the pipes of the first pattern that are facing the U-shape body and the legs of the U-shape body.
  • Relatively hot flue gas has a relatively large volume and vice versa.
  • the flue gas coming from the burner has a relatively large flow rate as the flue gas is relatively hot, thereby requiring a relatively large surface area between adjacent pipes arranged near the burner space in order to have the velocity of the flue gas being maximally said value C.
  • the pipes arranged near the outlet opening however require a smaller surface area there between in order to have the velocity of the flue gas being maximally said value C, as the flue gas is already cooled down to some extent by the heat exchanger and the flow rate is relatively small.
  • An advantage of a substantially constant velocity of the flue gas throughout the heat exchanger is that such a substantially constant velocity reduces the pressure drop. It is therefore an advantage of this embodiment to arrange said second part of the pipes such that this formula is fulfilled.
  • An advantage of this embodiment is that the heat exchanger is designed such that the distribution of the liquid flow over determined groups of pipes is chosen such that the quantity of heat Q discharged from the flue gas and transferred to the liquid flowing in each pipe is substantially constant anywhere in the heat exchanger.
  • the pipes are exposed to less thermal stresses as the pipes are exposed to more or less similar heat transfer.
  • the liquid flow through the pipes is optimized with respect to pressure drop and blockage of the pipes due to lime scale deposition is prevented by preventing the pipes from becoming too hot. This is especially advantageous in heat exchangers where a relatively large number of pipes with a relatively small throughflow area is used.
  • At least one of the connecting means comprises a liquid distributor for substantially equally distributing liquid over pipes being connected to said connecting means.
  • liquid distributor Without such a liquid distributor it is possible that the liquid is not equally distributed over the pipes connected to the connecting means. This way, some pipes with less liquid flowing there through can become too hot and thereby exposed to high thermal stresses.
  • An advantage of the liquid distributor is therefore that the liquid is substantially equally distributed over pipes that are connected to said connecting means, thereby reducing the thermal stresses of the pipes.
  • the second part of the pipes comprise at least three groups of pipes, wherein a first group located near the base of the U-shape body has a first, smallest diameter, wherein a second group located near the first group at a side of the first group opposite to the base of the U-shape has a second diameter, and wherein a third group located near the open end of the U-shape body has a third, largest diameter, which third group is located at a predetermined distance from the second group.
  • An advantage of this arrangement of the pipes is that the third group is arranged nearest to the burner space.
  • the flue gas coming from the burner is cooled down relatively fast by this third group of pipes arranged near the burner with relatively large diameter and thereby relatively large liquid flow, such that the production of NOx is efficiently reduced.
  • said predetermined distance is present, such that over this distance the flue gas is substantially not cooled down and a relatively large time period is provided for the conversion of CO into CO 2 , such that the emission of CO is reduced and preferably prevented.
  • said distance is preferably between 10 and 40mm, more preferably between 20 and 30mm. Said distance is defined between the outer surfaces of the row of pipes of the third group and the row of pipes of the second group arranged nearest to the third group and especially between the facing outer surfaces thereof.
  • a part of the pipes of the first group is arranged at least partly between a part of the pipes of the second group.
  • An advantage of such an arrangement is that the flow of flue gas along substantially the whole outer surface of the pipes arranged upstream of said part of pipes of the second group as seen in the direction of the flow of flue gases is enhanced.
  • the invention also relates to an assembly of a heat exchanger according to any of the claims 1 - 10 and a burner, wherein the burner is arranged in said receiving space.
  • the assembly comprises the heat exchanger according to at least claim 2, wherein the burner is arranged in said receiving space in such a manner that in use at least a part of the pipes of the first pattern surround a flame provided by said burner.
  • said burner comprises a damper.
  • Such a (Panel Helmholtz resonance) damper efficiently dampens any noise of the heat exchanger.
  • said burner comprises a burner plate that is connected to or is integrally formed with said damper.
  • An advantage of this embodiment is that the functions of the burner plate and the damper are combined in one integrally formed or connected element.
  • said burner comprises a gas/air-mixture distribution plate that is connected to or integrally formed with said damper and/or burner plate.
  • An advantage of this embodiment is that the functions of the burner plate and/or the damper and/or the gas/air-mixture distribution plate are combined in one integrally formed or connected element.
  • said (Panel Helmholtz resonance) damper may be provided with through holes for distributing the gas/air-mixture, such that said damper functions also as said gas/air-mixture distribution plate.
  • said assembly comprises a sealing that is provided between the casing and the gas/air-mixture distribution plate.
  • Said gas/air-mixture distribution plate is arranged upstream of the burner plate and distributes the gas/air-mixture prior to passing though the burner plate.
  • the gas/air-mixture distribution plate and the burner plate are connected or integrally formed in one element, the gas/air-mixture exiting the gas/air-mixture distribution plate cannot by-pass the burner plate.
  • Said sealing prevents the gas/air-mixture from entering the burner room alongside said element comprising the gas/air-mixture distribution plate and the burner plate.
  • the gas/air-mixture flowing through the gas/air chamber will cool down the gas/air chamber and the gas/air-mixture distribution plate/damper. The life time of the burner is hereby enhanced.
  • FIGS 1A and 1B show a heat exchanger 1.
  • Said heat exchanger 1 comprises a casing with a substantially U-shaped body 2 as seen in cross-section and extending in a longitudinal direction L.
  • the base 3 of the body 2 arranged at the lower end of the body 2 comprises a gas outlet opening (not shown).
  • the body 2 is open and comprises a receiving space 4 for receiving a burner (not shown).
  • the flue gases from the burner flow downwards through the casing 1 and are discharged via said gas outlet opening.
  • the body 2 comprises an end plate 6.
  • a plurality of pipes 9 is arranged within said casing and is connected to said end plates 6, in particular to holes in said end plates 6.
  • a liquid practically water flows though the pipes 9 for taking up heat from the flue gases, thereby heating the water and cooling the flue gases.
  • Panels 7 are provided to cover the end plates 6.
  • Each panel 7 comprises a plurality of hollow spaces 8, each hollow space 8 connecting at least two pipes 9 at each longitudinal end zone 5 of the body 2, such that liquid flowing through a first pipe 9 of the at least two pipes 9 is directed to the other pipe 9 of the at least two pipes 9. Liquid flowing through the pipes 9 thereby flows from the one longitudinal end zone 5 to the other longitudinal end zone 5 via the plurality of pipes 9 and hollow spaces 8.
  • a water inlet 10 and a water outlet 11 are provided in one panel 7 at one longitudinal end zone 5, for feeding relatively cold water to the pipes 9 via the water inlet 10 and for discharging relatively hot water from the pipes 9 via the water outlet 11.
  • Said hot water may be used for central heating or tap water.
  • a first part of the pipes 9 is arranged in a first pattern 12 defining two legs of a substantially U-shape as seen in cross-section, said first pattern being arranged substantially parallel to legs of said U-shape body 2.
  • the receiving space 4 for the burner is arranged between at least a part of the pipes 9 of the first pattern 12 located near the open end of the body 2 in such a manner that in use at least a part of the pipes 9 of the first pattern 12 surround a flame provided by said burner. This way, said part of the pipes 9 of the first pattern 12 protect the casing from the heat of the flame.
  • a distance between all pairs of adjacent pipes 9 of each leg of the first pattern 12 is preferably maximally 0.5 mm, more preferably maximally 0.1 mm, thereby restricting the mass flow of flue gas that will flow through the spaces between adjacent pipes 9 to an area between the pipes of the legs of the first pattern 12 and the casing, such that the flue gas that will enter this area will be cooled down by the liquid in the pipes 9 to such an extent that the flue gas will have a relatively low temperature that is more or less similar to or slightly higher than the temperature of the walls of these pipes 9.
  • the distance between the legs of the U-shape body 2 and the pipes 9 of the first pattern12 is preferably maximally 1.0 mm, more preferably maximally 0.4 mm, thereby also contributing to the restriction of the mass flow of flue gas into this area and thereby contributing to the reduction in temperature to which the casing is exposed.
  • a sealing 13 is arranged between the outer surface of the pipes 9 arranged at a first end of each leg of the first pattern 12 near the open end of the body 2 and the body 2, thereby sealing off the space there between and thereby preventing the flue gases from flowing in the area between the pipes 9 of the first pattern 12 and the casing via said space.
  • a second part of said pipes 9 are arranged within a space 14 at least partly bounded by said first pattern 12.
  • Relatively hot flue gas has a relatively large volume and vice versa.
  • the flue gas coming from the burner arranged in the receiving space 4 has a relatively large flow rate as the flue gas is relatively hot, thereby requiring a relatively large surface area between adjacent pipes 9 arranged near the burner space in order to have the velocity of the flue gas being maximally said value C.
  • the pipes 9 arranged near the outlet opening in the base 3 of the body 2 therefor require a smaller surface area there between in order to have the velocity of the flue gas being maximally said value C, as the flue gas is already cooled down to some extent by the heat exchanger and the flow rate is relatively small. This is shown in figure 1B , showing that the closer the pipes 9 are arranged to the burner arranged in the receiving space 4, the larger the surface area between the pipes 9.
  • the second part of the pipes comprises three groups of pipes 9, wherein a first group 15 located near the base 3 of the body 2 has a first, smallest diameter, wherein a second group 16 located near the first group 15 at a side of the first group 15 opposite to the base 3 of body 2 has a second, intermediate diameter, and wherein a third group 17 located near the open end of the body 2 has a third, largest diameter.
  • a third group 17 of pipes 9 has the largest diameter of the three groups, the flow rate of liquid flowing there through is also the largest of the three groups, thereby cooling down the flue gas coming from the burner relatively fast and efficiently reducing production of NO x .
  • the pipes 9 of the second group 16 have an intermediate diameter adapted to the amount of heat to be absorbed from the already partly cooled down flue gases, and the pipes 9 of the first group 15 have the smallest diameter adapted to absorb heat from the more cooled down flue gases.
  • a part of the pipes 9 of the first group 15, in particular three pipes 9 thereof, is arranged at least partly between a part of the pipes 9 of the second group 16, wherein said part of the pipes 9 of the first group 15 and said part of the pipes 9 of the second group 16 are arranged alternately in a direction substantially orthogonal to the direction of the flow of the flue gases.
  • the flow of flue gas is directed along substantially the whole outer surface, in particular also along the lower surface, of the pipes 9 arranged directly upstream of said part of pipes 9 of the second group 16 as seen in the direction of the flow of flue gases.
  • FIG. 2 schematically shows the distribution of the liquid flow through the pipes 9 of the heat exchanger. This shows that the pipes 9 are divided over in total twenty-two groups. Appointment of the pipes 9 to each group is established with said hollow spaces 8 that connect any desired number of selected pipes 9 to a specific group.
  • Liquid enters the first group I via the liquid inlet 10 that is in medium through flow connection with group I and exits the last group XX via liquid outlet 11 that is in medium through flow connection with group XX.
  • the liquid flows alternatingly between the two end zones 5 via the groups in sequential order, thus via group I to group II, from group II to group III, etc.
  • the number of pipes 9 belonging to each group and the selection of pipes 9 belonging to each group may be chosen as desired.
  • the selection and number of pipes 9 belonging to each group are chosen to fulfil a second formula:
  • the liquid flow is distributed such that the quantity of heat Q discharged from the flue gas and transferred to the liquid flowing in each pipe is substantially constant anywhere in the heat exchanger.
  • Figures 3A and 3B show the effect of liquid distributors according to the invention.
  • Said liquid distributors may be provided in any desired hollow space 8 for distributing the liquid over the pipes 9 connecting to that hollow space 8.
  • Figure 3A shows a plurality of three pipes 9 of a group that are connected via a hollow space 8 to three pipes 9 of a subsequent group. The liquid tends to follow the largest curvature and thereby to enter the most outer pipe 9 of the three pipes of the subsequent group. The middle pipe therefor receives less liquid and will therefor become relative hot and exposed to high thermal stresses.
  • each pipe 9 of a group is connected to a pipe 9 of the subsequent group. The liquid is thereby evenly distributed over the pipes 9 belonging to a specific group, independent of the location of the pipe 9.
  • FIG 4 is a perspective view of a burner according to the invention.
  • Said burner comprises a casing 18.
  • an element comprising a ceramic burner plate 19 and a damper 21 that also functions as an aluminium gas/air mixture distribution plate and that is arranged upstream from the burner plate 19.
  • An anorganic insulation material 20 is provided between the burner plate 19 and the damper/distribution plate 21.
  • a sealing 22 is provided between the casing 18 and the damper/distribution plate 21, such that the gas/air-mixture is prevented from entering the burner room alongside said element comprising the damper/distribution plate 21 and the burner plate 19.
  • the gas/air-mixture exiting the damper/distribution plate 21 cannot by-pass the burner plate 19.
  • the gas/air-mixture flowing through the gas/air chamber will cool down the gas/air chamber and the gas/air-mixture distribution plate/damper 21.
  • the life time of the burner is hereby enhanced.
  • Figure 5 shows an assembly of the heat exchanger of figures 1A , 1B and the burner of figure 4 .
  • the U-shape body 2 and the panels 7 of the heat exchanger are shown, as well as the casing 18 of the burner.
  • the burner is arranged such in the receiving space of the body 2, that the flames coming from the burner plate are surrounded by the upper pipes 9 of the legs of the first pattern 12 of pipes 9.

Landscapes

  • 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)
EP16159342.1A 2015-03-10 2016-03-09 Wärmeübertrager und anordnung eines wärmetauschers und eines brenners Pending EP3076101A3 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
NL2014432A NL2014432B1 (en) 2015-03-10 2015-03-10 Heat exchanger and assembly of a heat exchanger and a burner.

Publications (2)

Publication Number Publication Date
EP3076101A2 true EP3076101A2 (de) 2016-10-05
EP3076101A3 EP3076101A3 (de) 2018-03-28

Family

ID=53502764

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16159342.1A Pending EP3076101A3 (de) 2015-03-10 2016-03-09 Wärmeübertrager und anordnung eines wärmetauschers und eines brenners

Country Status (2)

Country Link
EP (1) EP3076101A3 (de)
NL (1) NL2014432B1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017212965A1 (de) * 2017-07-27 2019-01-31 smk systeme metall kunststoff gmbh & co. kg Wärmetauscher für eine Gastherme
CN110529840A (zh) * 2019-08-22 2019-12-03 嘉兴市建超智能科技有限公司 一种燃气锅炉本体

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0687870B1 (de) 1994-06-15 2000-01-12 Atag Verwarming B.V. Wärmetauscher

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2499223B1 (fr) * 1979-11-23 1985-06-28 Landreau Andre Chaudiere, notamment pour installation de chauffage
NL8105827A (nl) * 1981-12-23 1983-07-18 Remeha Fabrieken Bv Verwarmingsketel.
GB2244799A (en) * 1990-05-30 1991-12-11 Welmark Limited Boiler unit
AT396981B (de) * 1991-09-12 1994-01-25 Vaillant Gmbh Lamellenwärmetauscher
IT1295238B1 (it) * 1997-09-29 1999-05-04 Ferroli Spa Caldaia perfezionata premiscelata a condensazione,particolarmente idonea alla produzione di acqua sanitaria e per riscaldamento
ITPR20010024A1 (it) * 2001-03-23 2002-09-23 Immergas Spa Scambiatore di calore in caldaia a condensazione.
DE102009028624A1 (de) * 2009-08-18 2011-02-24 Sandvik Intellectual Property Ab Strahlungsbrenner

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0687870B1 (de) 1994-06-15 2000-01-12 Atag Verwarming B.V. Wärmetauscher

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102017212965A1 (de) * 2017-07-27 2019-01-31 smk systeme metall kunststoff gmbh & co. kg Wärmetauscher für eine Gastherme
DE102017212965B4 (de) * 2017-07-27 2020-11-05 smk systeme metall kunststoff gmbh & co. kg Wärmetauscher für eine Gastherme
CN110529840A (zh) * 2019-08-22 2019-12-03 嘉兴市建超智能科技有限公司 一种燃气锅炉本体

Also Published As

Publication number Publication date
NL2014432B1 (en) 2017-01-06
NL2014432A (en) 2016-10-10
EP3076101A3 (de) 2018-03-28

Similar Documents

Publication Publication Date Title
US11585572B2 (en) Heat exchanger unit and condensing boiler using the same
US11287158B2 (en) Heat exchanger and hot water apparatus
CN108369029B (zh) 基于冷凝方式的燃烧设备
EA201190265A1 (ru) Теплообменник
EP3076101A2 (de) Wärmeübertrager und anordnung eines wärmetauschers und eines brenners
US11835261B2 (en) Heat exchanger unit
UA98821C2 (ru) Теплообменник плоского типа
EP2307816B1 (de) Kondensationsbrennrohrkessel zum herstellen von warmem wasser
US20210247102A1 (en) Heat-exchange pipe, heat-exchanger unit using same, and condensing boiler using same
US4182276A (en) Economizer for smoke tube boilers for high pressure steam and hot water
JP5731936B2 (ja) 給湯器
JP2017083048A (ja) 熱交換器、二次熱交換器および熱源機
CA2983181C (en) Alternative coil for fired process heater
RU2296921C2 (ru) Подогреватель жидких или газообразных сред
PL91719B1 (de)
RU169049U1 (ru) Дымоход - теплообменник
KR101180241B1 (ko) 용융로
RU2145044C1 (ru) Воздухонагреватель
CN202813421U (zh) 一种空气预热器烟气入口非平衡换热器
CN210241963U (zh) 一种具有水路同程管路的燃气热水炉
CN213542467U (zh) 水冷燃烧器及具有其的燃气热水器
RU37803U1 (ru) Водогрейный водотрубный котел
US8771475B1 (en) Intertwined tube coil arrangement for a delayed coker heater
US2292682A (en) Heating of fluid
RU2236648C1 (ru) Водогрейный котел

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): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

RIC1 Information provided on ipc code assigned before grant

Ipc: F28D 7/00 20060101ALI20180220BHEP

Ipc: F24H 1/40 20060101AFI20180220BHEP

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

Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE

17P Request for examination filed

Effective date: 20180928

RBV Designated contracting states (corrected)

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

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

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20200414

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

Free format text: STATUS: EXAMINATION IS IN PROGRESS

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: ATAG HEATING B.V.