EP1843101A2 - Wärmetauschervorrichtung eines Gasbrenners - Google Patents

Wärmetauschervorrichtung eines Gasbrenners Download PDF

Info

Publication number
EP1843101A2
EP1843101A2 EP20070105523 EP07105523A EP1843101A2 EP 1843101 A2 EP1843101 A2 EP 1843101A2 EP 20070105523 EP20070105523 EP 20070105523 EP 07105523 A EP07105523 A EP 07105523A EP 1843101 A2 EP1843101 A2 EP 1843101A2
Authority
EP
European Patent Office
Prior art keywords
small diameter
tubular portion
diameter
heat exchanger
pipes
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
EP20070105523
Other languages
English (en)
French (fr)
Other versions
EP1843101A3 (de
EP1843101B1 (de
Inventor
Dominique Michaud
Yves Lubrina
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.)
Thirode Grandes Cuisines Poligny SAS
Original Assignee
Thirode Grandes Cuisines Poligny SAS
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=37719389&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP1843101(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Thirode Grandes Cuisines Poligny SAS filed Critical Thirode Grandes Cuisines Poligny SAS
Publication of EP1843101A2 publication Critical patent/EP1843101A2/de
Publication of EP1843101A3 publication Critical patent/EP1843101A3/de
Application granted granted Critical
Publication of EP1843101B1 publication Critical patent/EP1843101B1/de
Revoked legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24C—DOMESTIC STOVES OR RANGES ; DETAILS OF DOMESTIC STOVES OR RANGES, OF GENERAL APPLICATION
    • F24C15/00—Details
    • F24C15/32—Arrangements of ducts for hot gases, e.g. in or around baking ovens
    • F24C15/322—Arrangements of ducts for hot gases, e.g. in or around baking ovens with forced circulation
    • 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
    • F28D7/08—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 otherwise bent, e.g. in a serpentine or zig-zag
    • 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
    • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators

Definitions

  • the invention relates to the field of heat exchangers, more particularly the heat exchangers arranged downstream of a gas burner.
  • EP 0 103 526 discloses a convection oven comprising a heating compartment, a gas burner, heat exchangers for conducting combustion products from the gas burner, a convection blower for blowing air over the heat exchangers, and in the heating compartment.
  • the fan draws air out of the heating compartment, for recirculation through the heat exchanger into the heating compartment.
  • the heat exchanger includes a pipe for conducting the flame and the combustion products of the burner downstream. The heat exchanger is arranged between the heating compartment and the fan.
  • Such an oven is relatively bulky in depth.
  • the diameter of the heat exchanger pipe must be calculated according to the burner output and increase if a more powerful burner is used.
  • EP 0 519 303 discloses a heat exchanger for hot air consisting of several bolted parts together, including an outer chamber, a preliminary chamber, a base, two straight heat exchange tubes opening into an exhaust tube via seals graphite sealing.
  • Such an exchanger has the same disadvantages as those of the previous document and is also particularly complicated and expensive to manufacture, while providing a relatively low heat exchange surface.
  • the document EP 0 856 705 describes a monotube heat exchanger. The pressure drops are high and the temperature is not homogeneous.
  • the document US 5,301,654 describes an S-shaped heat exchanger.
  • the temperature is inhomogeneous.
  • the size is high.
  • the present invention aims to overcome the disadvantages mentioned above.
  • the present invention proposes a heat exchanger allowing a particularly compact furnace architecture, adaptable to furnaces of different powers and of different dimensions with standard elements providing a good distribution of heat and can be manufactured relatively economically.
  • the kitchen oven gas burner heat exchanger device comprises a large diameter combustion chamber tubular part, two small diameter pipes arranged at least partly parallel to each other and a biconical connection trunk. Between the tubular part of large diameter and small diameter pipes.
  • the biconical connecting trunk is attached to the large diameter tubular part and to the small diameter pipes.
  • the tubular portion of large diameter, the biconical connecting trunk and at least one small diameter pipe form an open ring, leaving free a central space delimited at least by a longitudinal face of the tubular portion of large diameter and at least one longitudinal face at least one pipe of small diameter.
  • the open ring shape is particularly advantageous in terms of reducing the effects of thermal expansion.
  • the dimensions of the heat exchanger are slightly increased between the state of rest and the state of operation. This could result in excessive stress on heat exchanger supports and / or on the oven frame with the risk of deformation and rupture.
  • the open ring shape with upstream and downstream ends close to each other makes it possible to very greatly reduce these risks.
  • the heat exchanger may comprise a small diameter pipe portion parallel to the tubular portion of large diameter and substantially equal length, resulting in a substantially equal elongation during operation.
  • two small diameter pipe portions substantially perpendicular to the tubular portion of large diameter may have substantially equal lengths, resulting in a substantially equal elongation during operation.
  • the open ring shape and the presence of small diameter pipe portions allows a certain elasticity of the heat exchanger in the direction of the opening of the ring, resulting in reduced forces exerted by the exchanger thermal on its supports.
  • the tubular portion of large diameter and the biconical connecting trunk are symmetrical with respect to two perpendicular planes passing through the geometric axis of the tubular portion of large diameter.
  • the perpendicular planes can be respectively vertical and horizontal.
  • the small diameter pipes may be superimposed or juxtaposed near the biconical connecting trunk. It is possible to make separate versions comprising identical parts which are connected in different ways.
  • the tubular portion has a diameter of between 2 and 2.5 times the diameter of the small diameter pipes.
  • the tubular portion of large diameter allows efficient combustion, while the small diameter pipes allow a high heat exchange to the extent that the ratio of their circumference on their section is higher than that of the tubular portion of large diameter. This promotes a more homogeneous heat exchange along the heat exchanger, insofar as the temperature of the gases in the large diameter tubular portion is higher than in the small diameter pipes arranged downstream.
  • the small diameter pipes comprise at least one bend of radius of curvature of between 3 and 5 times the diameter of the small diameter pipes. Such a radius of curvature allows a satisfactory mixture of gases within the small diameter pipes and therefore a quality heat exchange while leaving free a sufficient central space.
  • At least one pipe of small diameter comprises a first straight portion disposed in the extension of the tubular portion of large diameter, a first elbow, a second straight portion, a second elbow, a third straight portion substantially parallel to the tubular part of large diameter, a third elbow and a fourth straight portion.
  • the second straight portion may be substantially perpendicular to the tubular portion of large diameter.
  • the fourth straight portion may have an angle between 70 and 85 ° relative to the tubular portion of large diameter.
  • the first and second elbows may be substantially 90 °.
  • the first straight portion may have a small length, for example less than 10% of the length of the tubular portion of large diameter or of the order of 5 to 20% of the length of the third straight portion.
  • the first bend of a small diameter pipe and the first bend of the other small diameter pipe are oriented in opposite directions, the small diameter pipes being substantially identical.
  • the heat exchanger has an 8-digit shape with the large diameter tubular portion disposed substantially centrally and the small diameter pipes extending upward and downwardly from the biconical trunk of connection disposed in the extension of the tubular portion of large diameter. This promotes a good distribution of heat.
  • Two blowers can be provided for a heat exchanger.
  • the tubular portion and the biconical connecting trunk are symmetrical with respect to two perpendicular planes passing through the geometric axis of the tubular portion.
  • the small diameter pipes are symmetrical with respect to one of said two planes.
  • the second straight portions of the small diameter pipes are of different lengths to clear two central spaces.
  • the small diameter pipes are substantially parallel and open into a common header. Small diameter pipes can be supported by common supports. This arrangement is well suited to small furnaces.
  • At least one small diameter pipe includes a downstream end disposed near the large diameter tubular portion.
  • the heat exchanger thus forms an open loop around a central space left free.
  • a circle inscribed in said central space has a diameter greater than 2 times, preferably 2.5 times, the diameter of the tubular portion of large diameter.
  • the gas oven comprises a thermal enclosure, the heat exchanger disposed in the thermal enclosure and a fan also disposed in the thermal enclosure.
  • the heat exchanger is arranged around the fan and comprises a tubular portion of large diameter forming a combustion chamber, two small diameter pipes arranged at least partly parallel to each other and a biconical trunk connecting the part Tubular large diameter and small diameter pipes.
  • the biconical connecting trunk is attached to the tubular part of large diameter and to the small diameter duct.
  • the tubular portion of large diameter, the biconical connecting trunk, and at least one small-diameter pipe form an open ring disposed around the fan, at least one longitudinal face of the tubular portion of large diameter and at least one longitudinal face d at least one small diameter pipe facing said blower.
  • the oven can be particularly compact in the sense of depth, in the heat exchanger and the fan are arranged in the same geometrical envelope in the direction of the thickness of the furnace.
  • the power of a burner can range from 8 to 40 kW, it is possible to provide a very wide range of furnace, for example from 8 to 80 or even 120 kW using heat exchangers either identical or with many common parts, where standardization allows economies of scale.
  • the variant with three blowers and two heat exchangers is interesting for a high power furnace.
  • the tubular portions of large diameter may be disposed at the upper and lower ends of the enclosure.
  • Each heat exchanger may comprise a small diameter pipe passing between the low and medium blowers and a small diameter pipe passing between the high and medium blowers.
  • the two heat exchangers can be identical and mounted head to tail.
  • the thermal enclosure comprises a cooking chamber, a heating chamber and a partition wall provided with openings.
  • the blower and the heat exchanger are arranged in the heating chamber.
  • the openings of the partition wall make it possible to let the gases heated by the heat exchanger and circulated by the fan.
  • a heat exchanger can be arranged in the same space as electrical resistors mounted in the case of an electric furnace.
  • An electric oven and a gas oven can thus benefit from an increased number of common parts, in particular mechanical parts, such as the frame, the side walls, the lower and upper walls, which allows a better standardization and consequently a decrease in unit costs.
  • the use of a gas oven is facilitated, especially in the case of a kitchen where the available space is low, which is advantageous to the extent that the gas is generally less expensive energy than electricity. This allows the user to make substantial savings.
  • the heat exchanger 1 comprises a tubular portion of large diameter 2, a biconical connecting trunk 3 and two small diameter pipes 4 and 5.
  • the tubular portion 2 is cylindrical and fixed , for example by welding, to the connecting trunk 3.
  • the tubular portion 2 and the connecting trunk 3 are monobloc.
  • the connecting trunk 3 comprises an end comprising a circular opening connected to the tubular part 2 and an opposite end comprising two circular openings of small diameter connected respectively to the lines 4 and 5.
  • the mutual attachment of the connecting trunk 3 and the lines 4 and 5 can be performed by welding.
  • the tubular portion 2 and the truncated conical trunk 3 are symmetrical with respect to two perpendicular planes passing the geometric axis of the tubular portion 2.
  • One of the planes passes through the geometric axes of lines 4 and 5. This plane is here horizontal.
  • the other plane passes between the pipes 4 and 5.
  • upstream and downstream will be used in the flow direction of the gases in the heat exchanger 1 during its operation.
  • the heat exchanger 1 comprises a radial plate 6 and provided with a plurality of holes for housing screws 7 for fixing the heat exchanger 1 on a support, for example an oven frame or a burner.
  • the heat exchange 1 is intended to be mounted downstream of a gas burner. The flame of the burner may extend into the combustion chamber formed by the tubular portion 2.
  • the heat exchanger 1 comprises a common exhaust manifold 8 with an axis perpendicular to the tubular portion 2 while being disposed in proximity, for example at a distance less than the diameter of said tubular portion 2.
  • the collector 8 is also perpendicular to the downstream end of the lines 4 and 5.
  • the manifold 8 comprises a short tubular portion open at one end and closed at the other end, the open portion being provided with a plate 9 for attachment to a support, for example the frame of the oven.
  • the collector 8 and the plate 9 can be welded together.
  • the manifold 8 and the lines 4 and 5 can be welded together.
  • each duct 4, 5 comprises a first straight portion 4a, 5a, of short length, whose upstream end is fixed to the downstream end of the connecting trunk 3, for example by welding, a first elbow 4b, 5b having an angle of the order of 90 °, a second straight portion 4c, 5c significantly longer than the first straight portion 4a, 5a, a second elbow 4d, 5d, a second straight portion 4e, 5e parallel to the tubular portion 2, a third bend 4f, 5f, for example having an angle of the order of 70 to 85 °, and a fourth straight portion 4g, 5g whose downstream end opens into the manifold 8.
  • the bend 4d, 5d also has an angle of the order of 90 °.
  • the length of the second straight portion 4c, 5c and the third straight portion 4e, 5e is substantially equal to the length of the tubular portion 2.
  • the length of the fourth straight portion 4g, 5g is significantly lower, for example order of 50 to 75% of the length of the tubular portion 2.
  • the heat exchanger is completed by one or more spacers 10, disposed between the pipes 4 and 5, and to maintain their spacing, especially during handling prior to final assembly in an oven.
  • the heat exchanger 1 also comprises an attachment lug 11 making it possible to fix the heat exchanger 1 on a support, in particular at the level of the pipes 4, 5.
  • the gases flow horizontally in one direction in the tubular part 2, then in the connecting trunk 3, then in the first straight portion 4a, 5a, by being distributed between the two lines 4 and 5.
  • the gases then pass into the first elbow 4b, then descend into the second straight portion 4c, pass into the second elbow 4d, circulate substantially horizontally in the third straight portion 4e, but in a direction opposite to that of the flow.
  • in the tubular portion 2 pass into the third bend 4f, 5f, then back in the fourth straight portion 4g, 5g, and finally evacuate through the collector 8.
  • the gases therefore perform a path in the counterclockwise direction.
  • the heat exchanger 1 is generally formed of mechanically welded parts.
  • the pipes 4 and 5 may themselves be formed of mechanically welded parts or a bent tube at the desired angles.
  • the heat exchanger 1 has the shape of an open ring leaving a large central free space, which is very interesting in terms of compactness.
  • the collector 8 is disposed near the upstream end of the tubular portion 2, resulting in a large total length which allows a high heat exchange and hence a small effect of the thermal expansion which causes little stress on the support of the heat exchanger, in particular via the plates 6 and 9 due to the substantially identical expansion in length and height of the various components of the heat exchanger. More specifically, the expansion of the tubular portion 2, the connecting trunk 3 and the first straight portion 4a is substantially identical to the expansion of the third straight portion 4e, 5e.
  • the expansion of the second straight portion 4c is relatively close to that of the fourth straight portion 4g.
  • the open ring shape gives the heat exchanger 1 some elasticity, in that the distance between the plates 6 and 9 may vary slightly in the unmounted state illustrated in FIG. expansion in the mounted state, this results in low forces exerted by the plates 6 and 9 on the frame.
  • a fan 12 or a relatively high diameter turbine may be mounted in the central space left free by the heat exchanger.
  • the blower 12 may be of centrifugal type, sucking the air by its center and pushing it by its periphery and thus forcing air to pass around the tubular part 2 or ducts 4 and 5.
  • the connecting trunk 3 is better visible.
  • the connecting trunk 3 comprises an upstream inlet of the same axis as the tubular part 2 and two downstream outlets 3a and 3b, with axes parallel to the axis of the tubular part 2.
  • the connecting trunk 3 can be obtained by clamping the end of a portion of tube.
  • the outlets 3a and 3b of the connecting trunk 3 are separated radially by a small space closed by the nip of the sheet forming the tube and the bringing together and welding of two ends diametrically opposed to form a junction zone 13.
  • a tubular portion of diameter between 2 and 2.5 times the diameter of the small diameter pipes Preferably, a diameter of the upper tubular portion of at least a few percent to two times the diameter of the small diameter pipes 4 and 5 will be selected.
  • a furnace 14 for cooking food products for example a large kitchen oven, comprises a frame 15 closed on five sides and a door 16 making it possible to open or close the sixth side to define an enclosure. 17.
  • the enclosure 17 is divided into a cooking chamber 18 disposed near the door 16 and a heating chamber 19 disposed on the opposite side, at the bottom of the enclosure 17.
  • the cooking chamber 18 and the heating chamber 19 are separated by a wall 20, removable, for example sheet metal thin, and pierced with openings at its center and at its ends.
  • the cooking chamber 18 may be arranged a plurality of supports 21, or a carriage, for supporting the food to be cooked 22.
  • the oven 14 comprises, disposed in the heating chamber 19, a heat exchanger 1. are visible in Figure 4, the tubular portion 2 of the heat exchanger 1 in the upper part and the pipes 4 and 5 in the lower part.
  • a fan 12 which can be driven by a motor 24 disposed behind the heating chamber 19, for example in the frame 15.
  • the fan 12 centrifugal type, is able to suck the air through at least one central opening provided in the wall 20, then to discharge it radially to the heat exchanger 1.
  • the heated air then passes into the cooking chamber 18 through end openings of the wall 20. thus obtaining a circulation of hot air in the enclosure 17, which allows a very rapid temperature rise of the furnace 14.
  • the size of the heating chamber 19 is particularly small and it is thus possible to make a furnace 14 of reduced depth while maintaining a cooking chamber 18 of depth unchanged. This reduces the size of the oven, which is particularly interesting in the case of kitchens of small area.
  • the heat exchanger 1 has an overall shape of 8 digit.
  • the tubular portion 2 and the connecting trunk 3 are similar to those of the previous embodiments.
  • the pipe 4 comprises straight portions 4a, 4c, 4e and 4g and bends 4b, 4d and 4f similar to those of the previous embodiments, except that the third bend 4f is substantially 90 °.
  • the right portion 4g is substantially parallel to the straight portion 4c and opens into a common manifold 25.
  • the tubular portion 2, the connecting trunk 3 and the duct 4 close the central space in which the fan 12 is disposed with the exception a small gap between the collector 25 and the tubular portion 2.
  • the pipe 5 comprises a first straight portion 5a and a first bend 5b, identical to those of the previous embodiments and hidden in the figure by the corresponding portions of the pipe 4.
  • the pipe 5 also comprises a second straight portion 5c of great length , for example of the order of twice the length of the second straight portion 4c of the pipe 4, a second elbow 5d, a third straight portion 5e, a third elbow 5f and a fourth straight portion 5g opening into the common header 25
  • the second bend 5d and the third straight portion 5e may be identical to those of the previous embodiments.
  • the third bend 5f has an angle of the order of 90 °.
  • the fourth straight portion 5g is substantially parallel to the second straight portion 5c and extends towards the plate 6 from the downstream end of the third bend 5f.
  • the length of the fourth straight portion 5g is approximately equal to the length of the second straight portion 5c.
  • the straight portions 5c, 5e and 5g and the bends 5d and 5f of the pipe 5, and the third straight portion 4e of the pipe 4 define an additional central space of generally rectangular shape, in which is disposed an additional turbine 26 .
  • the pipe 5 has a much greater length than that of the previous embodiments, the total heat exchange surface of the heat exchanger 1 is increased, which makes it possible to associate the heat exchanger 1 with a burner of higher power, for example of the order of 15 to 40 kW, while the heat exchanger 1 of the previous embodiments may be associated with a burner with a power of the order of 8 to 20 kW.
  • a double heat exchanger for a furnace of large capacity comprising a heat exchanger 1 which may be identical to that illustrated in FIG. 5 and an additional heat exchanger 27 which can be identical to the previous while being mounted upside down. More specifically, the plates 6 of the two heat exchangers 1 and 27 are coplanar. The collectors 25 are arranged on the same side, The size of the assembly in the direction of the axis of the turbines is preserved, thanks to the fact that each heat exchanger 1, 27 comprises a single pipe in the vicinity of the turbine 26. heat exchanger 27 releases a central space near the tubular portion 2, for housing a third turbine 28.
  • the turbine 26, which is centrally located between the turbines 12 and 28, is surrounded by two loops, a first loop formed by the third straight portion 4e of the pipe 4, the lower end of the second straight portion 5c, the second bend 5d, the third straight portion 5e, the third bend 5f and the lower end of the fourth straight portion 5g of the pipe 5 of the heat exchanger 1 and the same parts of the additional heat exchanger 27.
  • the pipe 5 of the heat exchanger 1 is mounted behind and the pipe 5 of the heat exchanger 27 is mounted forward allowing a shift in the direction of the depth, as can be seen in Figure 7.
  • the pipe 4 of the heat exchanger 1 is disposed on the front side of the furnace, while the pipe 4 of the heat exchanger 27 is disposed on the rear side.
  • This embodiment is perfectly suitable for ovens of large dimensions, for example at twenty levels and high power, for example from 40 to 80 kW.
  • the heat exchanger 1 comprises the same parts as the exchanger of FIGS. 1 to 4. The following description may be completed by that relating to FIGS. 1 to 4. These parts are assembled so as to form two rings open to accommodate one or two unrepresented turbines.
  • the heat exchanger 1 comprises the tubular portion of large diameter 2, the biconical connecting trunk 3 and the two small diameter pipes 4 and 5.
  • the tubular portion 2 is cylindrical of revolution and fixed, for example by welding, to the connecting trunk 3.
  • the tubular portion 2 and the connecting trunk 3 are monobloc.
  • the connecting trunk 3 comprises an end comprising a circular opening connected to the tubular part 2 and an opposite end comprising two small diameter circular openings connected respectively to the lines 4 and 5.
  • the geometric axes of the two small diameter circular openings and the geometric axis of the tubular portion 2 are parallel and / or coplanar.
  • the mutual attachment of the connecting trunk 3 and the lines 4 and 5 can be performed by welding.
  • the two circular openings of small diameter of the connecting trunk 3 are aligned vertically. In other words, the geometric axes of the two circular openings of small diameter are arranged in a vertical plane.
  • the downstream end of the tubular portion 2 opens into the upstream end of the connecting trunk 3.
  • the downstream end of the connecting trunk 3 opens into the upstream end of the pipes 4 and 5.
  • the heat exchanger 1 comprises an exhaust manifold 8 having an axis perpendicular to the tubular portion 2 while being disposed close to it, for example at a distance less than the diameter of said tubular portion 2.
  • the collectors 8 are perpendicular to the downstream end of the lines 4 and 5.
  • the collector 8 and the pipe 4, 5 corresponding can be welded together.
  • the two lines 4 and 5 are identical and symmetrical with respect to a horizontal plane passing through the geometric axis of the tubular portion 2. This arrangement allows standardization of parts and assembly.
  • the pipe 4 is disposed in the high position and the pipe 5 is disposed in the low position.
  • the pipe 4 From upstream to downstream, the pipe 4 comprises a first straight portion 4a of short length, whose upstream end is fixed to the downstream end of the connecting trunk 3, for example by welding, a first bend 4b having a the order of 90 °, a second straight portion 4c directed upwards, a second elbow 4d, a second straight portion 4th parallel to the tubular portion 2, a third elbow 4f for example having an angle of the order of 70 to 85 °, and a fourth straight portion 4g directed downwards and whose downstream end opens into the manifold 8.
  • the pipe 4 defines an upper central space.
  • the pipe 5 From upstream to downstream, the pipe 5 comprises a first straight portion 5a whose upstream end is fixed to the downstream end of the connecting trunk 3, a first bend 5b, a second straight portion 5c directed downwards, a second elbow 5d, a second straight portion 5e, a third elbow 5f, and a fourth straight portion 5g directed upwards and whose downstream end opens into the collector 8.
  • the pipe 5 defines a lower central space. There is an excellent distribution of heat in the oven. The theoretical pressure losses are equal in lines 4 and 5, resulting in substantially equal flow rates.
  • the collectors 8 of lines 4 and 5 are arranged at a small distance from one another, which makes it possible to easily connect them to a common evacuation.
  • Heat exchangers can therefore be manufactured by benefiting from longer series, which reduces unit costs.
  • the fact of benefiting from two separate pipes 4 and 5 allows a more homogeneous distribution of the heat, in particular in comparison with a monotube heat exchanger, of length equal to the sum of the lengths of the pipes 4 and 5. It has also been found that the fact of having two separate pipes formed in parallel in the direction of the gas flow, allows a reduction of the operating noise of the heat exchanger and a lowering of the resonance phenomena. The oven thus obtained is particularly silent.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Gas Burners (AREA)
EP20070105523 2006-04-03 2007-04-03 Wärmetauschervorrichtung eines Gasbrenners Revoked EP1843101B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR0602884A FR2899317A1 (fr) 2006-04-03 2006-04-03 Dispositif d'echangeur thermique de bruleur a gaz

Publications (3)

Publication Number Publication Date
EP1843101A2 true EP1843101A2 (de) 2007-10-10
EP1843101A3 EP1843101A3 (de) 2012-12-05
EP1843101B1 EP1843101B1 (de) 2014-02-26

Family

ID=37719389

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20070105523 Revoked EP1843101B1 (de) 2006-04-03 2007-04-03 Wärmetauschervorrichtung eines Gasbrenners

Country Status (2)

Country Link
EP (1) EP1843101B1 (de)
FR (1) FR2899317A1 (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2236038A1 (de) * 2009-04-03 2010-10-06 Eurofours Gargerät mit Wärmetauscher
ITTO20100632A1 (it) * 2010-07-21 2012-01-22 Premark Feg Llc Scambiatore di calore migliorato per un dispositivo di processamento di cibo e forno provvisto dello stesso
ITVE20110067A1 (it) * 2011-10-06 2013-04-07 Foinox S P A Scambiatore di calore per apparecchi di cottura a gas.
CN105143773A (zh) * 2013-06-07 2015-12-09 因诺恩股份有限公司 用于烹饪器具的热交换器
ITUB20159610A1 (it) * 2015-12-21 2017-06-21 Satengineering Sas Di Francesco Dursi & C Forno di cottura

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9372005B2 (en) 2012-11-30 2016-06-21 Alto-Shaam, Inc. Heat exchanger for oven
DE102018122053A1 (de) * 2018-09-10 2020-03-12 Rational Aktiengesellschaft Wärmetauschereinrichtung und Gargerät damit

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4043015A (en) * 1976-08-18 1977-08-23 Brazeway, Inc. Method of forming a header assembly
US4203392A (en) * 1978-03-03 1980-05-20 Mclane Jack S Heat exchanger
US4484561A (en) * 1982-09-14 1984-11-27 Crescent Metal Products, Inc. Gas convection oven
US4648377A (en) * 1986-05-01 1987-03-10 Hobart Corporation Gas convection oven and heat exchanger therefor
US5301654A (en) * 1992-07-29 1994-04-12 Consolidated Industries Corp. Heat-exchanger especially for forced air furnaces
FR2710401B1 (fr) * 1993-09-22 1995-11-24 Rosinox Four à gaz à brassage d'air chaud.
EP0856705B1 (de) * 1997-01-30 2002-02-20 Rational AG Wärmetauschereinrichtung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2236038A1 (de) * 2009-04-03 2010-10-06 Eurofours Gargerät mit Wärmetauscher
FR2943890A1 (fr) * 2009-04-03 2010-10-08 Eurofours Sa Four de boulangerie-patisserie.
ITTO20100632A1 (it) * 2010-07-21 2012-01-22 Premark Feg Llc Scambiatore di calore migliorato per un dispositivo di processamento di cibo e forno provvisto dello stesso
WO2012012479A1 (en) * 2010-07-21 2012-01-26 Premark Feg L.L.C. Food processing device with a heat exchanger
ITVE20110067A1 (it) * 2011-10-06 2013-04-07 Foinox S P A Scambiatore di calore per apparecchi di cottura a gas.
CN105143773A (zh) * 2013-06-07 2015-12-09 因诺恩股份有限公司 用于烹饪器具的热交换器
JP2016521345A (ja) * 2013-06-07 2016-07-21 イノエン インコーポレイテッド 調理機器用熱交換器
ITUB20159610A1 (it) * 2015-12-21 2017-06-21 Satengineering Sas Di Francesco Dursi & C Forno di cottura
WO2017109717A1 (en) * 2015-12-21 2017-06-29 Satengineering S.A.S. Di Francesco D'ursi & C. Oven

Also Published As

Publication number Publication date
EP1843101A3 (de) 2012-12-05
FR2899317A1 (fr) 2007-10-05
EP1843101B1 (de) 2014-02-26

Similar Documents

Publication Publication Date Title
EP1843101B1 (de) Wärmetauschervorrichtung eines Gasbrenners
EP2404112B1 (de) Tür mit eingebautem brenner für heizgerät
EP3405723B1 (de) Kondensationswärmetauscher mit einer wärmetauschervorrichtung
FR2678360A1 (fr) Appareil de chauffage avec bruleur catalytique.
EP2923152B1 (de) Vorrichtung zur verbesserung der verbrennung in einem kamin
WO2010010277A1 (fr) Diffuseur d'echappement pour turbine a gaz
EP3026348A1 (de) Gerät zum kochen mit gas, insbesondere gasherd
EP1366326B1 (de) Kondensierender wärmetauscher für einen kessel
FR2959000A1 (fr) Conduit pour un circuit d'evacuation des produits de combustion et d'alimentation en air comburant dans une installation de fumisterie
FR2514474A1 (fr) Dispositif de chauffage d'un bain d'huile
FR3017191A3 (fr) Dispositif de reception de chaleur
FR2710401A1 (fr) Four à gaz à brassage d'air chaud.
EP4048953B1 (de) Kamin mit aufgehängtem herd
BE1003590A3 (fr) Chaudiere a gaz amelioree pour montage mural du type a circulation d'air forcee et etancheite dans le local pour utilisation domestique.
EP2354745B1 (de) Hausanlage zur Rauchgasentlüftung
CH653115A5 (fr) Bruleur a gaz.
FR2513360A1 (fr) Dispositif de chauffage du type forme d'un radiateur a gaz mural, de faible puissance, et a circuit etanche et echangeur thermique a plaques utilise dans celui-ci
FR2558338A1 (fr) Four de cuisson
EP1897443A1 (de) Brotbackofen
FR2716957A3 (fr) Echangeur de chaleur de forme hélicoïdale dont les enroulements intérieur et extérieur sont en tube lisse et en tube nervuré.
BE383004A (de)
BE563673A (de)
BE475881A (de)
BE443741A (de)
FR2984996A1 (fr) Conduit recuperateur de chaleur

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 MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

17P Request for examination filed

Effective date: 20080321

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 MT NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK RS

RIC1 Information provided on ipc code assigned before grant

Ipc: F28F 1/00 20060101ALI20121029BHEP

Ipc: F24C 15/32 20060101AFI20121029BHEP

RIC1 Information provided on ipc code assigned before grant

Ipc: F24C 15/32 20060101AFI20130611BHEP

Ipc: F28D 7/08 20060101ALI20130611BHEP

Ipc: F28F 9/26 20060101ALI20130611BHEP

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 MT NL PL PT RO SE SI SK TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20130909

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 MT 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: AT

Ref legal event code: REF

Ref document number: 653840

Country of ref document: AT

Kind code of ref document: T

Effective date: 20140315

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: FRENCH

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 602007035179

Country of ref document: DE

Effective date: 20140410

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20140226

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 653840

Country of ref document: AT

Kind code of ref document: T

Effective date: 20140226

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: 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: 20140226

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: 20140626

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: 20140626

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: 20140226

Ref country code: AT

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: 20140226

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: 20140226

Ref country code: NL

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: 20140226

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: 20140226

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

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: 20140226

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

Ref country code: CZ

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: 20140226

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: 20140226

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: 20140226

Ref country code: DK

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: 20140226

REG Reference to a national code

Ref country code: DE

Ref legal event code: R026

Ref document number: 602007035179

Country of ref document: DE

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

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

Ref country code: ES

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: 20140226

Ref country code: LU

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: 20140403

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: 20140226

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: 20140226

Ref country code: SK

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: 20140226

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

26 Opposition filed

Opponent name: RATIONAL AKTIENGESELLSCHAFT

Effective date: 20141106

PLAX Notice of opposition and request to file observation + time limit sent

Free format text: ORIGINAL CODE: EPIDOSNOBS2

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: DE

Ref legal event code: R026

Ref document number: 602007035179

Country of ref document: DE

Effective date: 20141106

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

Ref country code: CH

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

Effective date: 20140430

Ref country code: LI

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

Effective date: 20140430

PLBB Reply of patent proprietor to notice(s) of opposition received

Free format text: ORIGINAL CODE: EPIDOSNOBS3

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: 20140403

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: 20140226

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

Ref country code: MT

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: 20140226

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 10

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

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: 20140226

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: 20140527

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

Ref country code: TR

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: 20140226

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: 20070403

Ref country code: BE

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: 20140430

REG Reference to a national code

Ref country code: DE

Ref legal event code: R064

Ref document number: 602007035179

Country of ref document: DE

Ref country code: DE

Ref legal event code: R103

Ref document number: 602007035179

Country of ref document: DE

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 11

RDAF Communication despatched that patent is revoked

Free format text: ORIGINAL CODE: EPIDOSNREV1

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

Free format text: STATUS: THE PATENT HAS BEEN GRANTED

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

Ref country code: GB

Payment date: 20170427

Year of fee payment: 11

Ref country code: FR

Payment date: 20170426

Year of fee payment: 11

Ref country code: DE

Payment date: 20170427

Year of fee payment: 11

RDAG Patent revoked

Free format text: ORIGINAL CODE: 0009271

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

Ref country code: IT

Payment date: 20170421

Year of fee payment: 11

27W Patent revoked

Effective date: 20170309

GBPR Gb: patent revoked under art. 102 of the ep convention designating the uk as contracting state

Effective date: 20170309

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

Free format text: STATUS: PATENT REVOKED