EP3578911B1 - Rohrwärmetauscher für einen backofen - Google Patents

Rohrwärmetauscher für einen backofen Download PDF

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Publication number
EP3578911B1
EP3578911B1 EP19176648.4A EP19176648A EP3578911B1 EP 3578911 B1 EP3578911 B1 EP 3578911B1 EP 19176648 A EP19176648 A EP 19176648A EP 3578911 B1 EP3578911 B1 EP 3578911B1
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EP
European Patent Office
Prior art keywords
pipe
heat exchanger
sections
coil line
oven
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
EP19176648.4A
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German (de)
English (en)
French (fr)
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EP3578911A1 (de
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.)
Werner and Pfleiderer Industrielle Backtechnik GmbH
Original Assignee
Werner and Pfleiderer Industrielle Backtechnik GmbH
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Application filed by Werner and Pfleiderer Industrielle Backtechnik GmbH filed Critical Werner and Pfleiderer Industrielle Backtechnik GmbH
Priority to PL19176648T priority Critical patent/PL3578911T3/pl
Publication of EP3578911A1 publication Critical patent/EP3578911A1/de
Application granted granted Critical
Publication of EP3578911B1 publication Critical patent/EP3578911B1/de
Active legal-status Critical Current
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Classifications

    • 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
    • F28F9/02—Header boxes; End plates
    • F28F9/0243—Header boxes having a circular cross-section
    • 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
    • F28D7/082—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 with serpentine or zig-zag configuration
    • F28D7/085—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 with serpentine or zig-zag configuration in the form of parallel conduits coupled by bent portions
    • F28D7/087—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 with serpentine or zig-zag configuration in the form of parallel conduits coupled by bent portions assembled in arrays, each array being arranged in the same plane
    • 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
    • F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
    • F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
    • F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
    • F28D1/047—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag
    • F28D1/0477—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being bent, e.g. in a serpentine or zig-zag the conduits being bent in a serpentine or zig-zag
    • 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
    • F28D3/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium flows in a continuous film, or trickles freely, over the conduits
    • F28D3/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium flows in a continuous film, or trickles freely, over the conduits with tubular conduits
    • 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
    • F28F9/001—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core
    • F28F9/002—Casings in the form of plate-like arrangements; Frames enclosing a heat exchange core with fastening means for other structures
    • 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
    • F28F9/02—Header boxes; End plates
    • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
    • F28F9/0224—Header boxes formed by sealing end plates into covers
    • 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
    • F28F9/02—Header boxes; End plates
    • F28F9/0246—Arrangements for connecting header boxes with flow lines

Definitions

  • the invention relates to a tubular heat exchanger for an oven.
  • the invention also relates to a method for producing a coil tubular heat exchanger and an oven module and an oven with at least one such tubular heat exchanger.
  • Tube heat exchangers of the type mentioned at the beginning are known from the market, for example, as flat tube coils or as pillow radiators.
  • a tubular heat exchanger is known from AT 27 736 B .
  • An oven is known from the DE-PS 927 861 .
  • a heat exchanger for a shower or bathtub is known from the CH 709 194 A2 .
  • the EP 0 144 040 discloses a tubular heat exchanger according to the preamble of claim 1 and describes a loop heat exchanger.
  • the AU 524 322 B2 discloses an air cooled heat exchanger.
  • the US 2004/0 069 470 A1 and the GB 16,746 describe different variants of heat exchangers.
  • a defined small distance between adjacent pipe sections of the pipe heat exchanger which is smaller than a pipe diameter, leads to an efficient heat transfer from the pipe sections leads to a fluid flowing through between adjacent pipe sections, for example by flowing air.
  • the advantages of heating the baking space by emitting radiation from the tubular heat exchanger can thus be combined with the advantages of convective heat transfer, in particular in a baking space heated by circulating air.
  • one of the heat transfer mechanisms “radiant heat” or “heat transfer to fluid flowing through” can then be dominant.
  • Thermal oil can be used as the heat transfer fluid.
  • the distance between adjacent pipe sections can be greater than 2% of the pipe diameter, can be greater than 3% and can, for example, be in the range of 5% of the pipe diameter.
  • the distance between adjacent pipe sections can be smaller than 20% of the pipe diameter, can be smaller than 15% and can be smaller than 10% of the pipe diameter.
  • An absolute distance between adjacent pipe sections of the pipe heat exchanger can be 2 mm.
  • the design as a coiled pipe heat exchanger simplifies the supply and discharge of the heat transfer fluid carried in the pipe sections.
  • the design of the serpentine tube heat exchanger with two serpentine conduit paths increases the flexibility of a conduit routing through the tube heat exchanger, which can then be adapted to production-related requirements and / or structural requirements, for example installation space requirements.
  • 180 ° deflection sections between two pipe sections of the same serpentine conduction path are led out of the arrangement plane for exactly one of the serpentine conduction paths.
  • 180 ° deflection sections leading out of the arrangement plane in this way avoid a space conflict between the deflection sections of the various snake conduction paths.
  • a passage extends between the tubular sections, which at most can be interrupted by mounting components along negligible extension sections, along the entire tubular section. This increases the effectiveness the heat transfer from the pipe sections to the fluid flowing between them is optimized.
  • the tubular heat exchanger can also have more than two serpentine conduction paths.
  • An arrangement of the pipe sections according to claim 4 can enlarge a minimum bending radius of the pipe forming the pipe sections within a respective serpentine conduction path. This simplifies the manufacture of the tubular heat exchanger.
  • An inlet-side Y-pipe piece according to claim 5 enables a common heat transfer fluid supply for the various coil line inlets.
  • a corresponding Y-pipe section can also be provided on the outlet side.
  • a further object of the invention is to provide a manufacturing method for a coiled pipe heat exchanger which has at least two coiled conduction paths.
  • this object is achieved by a production method with the steps specified in claim 7.
  • the advantages of the manufacturing process correspond to those which have already been explained above with reference to the coil pipe heat exchanger with the at least two coil line paths.
  • the snake tube heat exchanger can be manufactured from exactly one type of pipe by corresponding sequential bending and, if necessary, adding further pipes to pieces.
  • a method according to claim 8 enables the production of a snake tube heat exchanger according to claim 6.
  • the bending out of the bent out 180 ° deflection sections can take place with the aid of a corresponding tube bending device in the course of the production of the snake line paths.
  • a resulting bending angle can be in the range of 150 °, for example.
  • the pipe sections of the pipe heat exchanger can extend horizontally in the oven module or in the oven.
  • the pipe sections of the pipe heat exchanger can extend transversely to a conveying direction of the baked good through the oven module or the oven. This transverse extension can take place over a width of the entire baking chamber.
  • the pipe sections of the pipe heat exchanger can also extend in the conveying direction of the baked good.
  • the oven can be a continuous oven, in particular a tunnel oven.
  • the oven can consist of several oven modules be made, which can be constructed in particular in the same way.
  • Fig. 1 shows an overall side view of a tunnel oven 1 designed as a tunnel oven, with which, for example, long-life baked goods in the form of soft biscuits, hard biscuits or lye biscuits can be produced. Other baked goods, such as toast, can also be processed in the oven.
  • the oven 1 can also be used for roasting and, as a special application, drying or sterilization.
  • a total of eight oven modules 2 1 to 2 8 which belong to an upper continuous baking chamber, and eight oven modules 3 1 to 3 8 underneath, which belong to a lower continuous baking chamber of the continuous oven 1.
  • the oven modules are thus arranged on two levels.
  • the furnace modules 2 1 to 2 8 and 3 1 to 3 8 each have the same basic structure, in particular with regard to a support frame design and receptacles for add-on and built-in parts.
  • the furnace modules 2 1 to 2 8 and 3 1 to 3 8 have the same dimensions, that is, in terms of height, width and depth, each basically have the same space requirements.
  • the oven modules 2 1 to 2 8 and 3 1 to 3 8 are initially available as separate modules and are connected to one another when the oven 1 is assembled. In each of the oven modules 2 1 to 2 8 and 3 1 to 3 8 , heated circulating air is in each case conducted in a circuit via the heat exchangers described below.
  • the upper oven modules 2 1 to 2 8 are supported by the lower oven modules 3 1 to 3 8 .
  • the lower furnace modules 3 1 to 3 8 are supported by a machine floor.
  • a loading module 4 for the baked goods is arranged in the conveying direction, which in turn has two floors and communicates with the two continuous baking rooms.
  • Behind a final oven module 2 i and 3 i in the direction of baked goods is an output module 5 of the continuous oven 1 for taking over the baked goods from the continuous baking rooms and for dispensing them, which is also designed in two floors and again with communicates with the two continuous baking rooms.
  • the loading module 4 on the one hand and the output module 5 on the other hand close the circulating air circuit at the beginning and at the end of the continuous baking rooms.
  • the conveyor oven 1 is in the Fig. 1 shown interrupted to indicate that the number of furnace modules 2 i , 3 i can be greater than in the Fig. 1 shown.
  • the number N of furnace modules 2 i , 3 i can vary in practice, for example, between 5 and 20.
  • Baked goods to be baked enter the respective continuous baking chamber 7, 8 via the loading module 4, i.e. into the respective leading initial oven module 2 1 , 3 1 , pass through the respective continuous baking chamber 7, 8 along the baked good conveying direction 9 and enter via the output module 5 after having passed through the last final oven modules 2 i , 3 i from the continuous baking chambers 7, 8, completely baked again.
  • a cleaning opening 6a for some or all of the furnace modules 2 i , 3 i , a cleaning opening 6a, an inspection opening 6b and a steam opening 6c are also provided. Steaming / unloading of the respective baking chamber of the oven module 2 i , 3 i is possible via the respective damage opening 6c.
  • Fig. 2 shows a section through one of the oven modules using the oven module 2 1 as an example.
  • the conveying direction 9 is perpendicular to the cutting plane or plane of the drawing Fig. 2 .
  • Fig. 3 shows this in greater detail using the example of one of the furnace modules 2 i.
  • the furnace modules 3 i are constructed in the same way, so that it is sufficient to follow the detailed illustration Fig. 3 to show an example of one of the furnace modules 2 i.
  • the Fig. 2 are not to be found, is in this respect to the Fig. 3 referenced.
  • the oven modules 2 i , 3 i each have an oven 10, which is heated on the one hand directly via the circulating air and on the other hand via radiant heat, which is generated by heat exchangers in the form of two coil tube heat exchangers 11, 12.
  • the baking rooms 10 are each part of the two stacked through-going baking rooms 7, 8, which are formed on the one hand by the upper oven modules 2 i and on the other hand by the lower oven modules 3 i .
  • the tubular heat exchanger 11 arranged above the baking space generates top heat for the baking space 10.
  • the tubular heat exchanger 12 arranged below the baking space generates bottom heat for the baking space 10.
  • Thermal oil is used as the heat transfer fluid that flows through the tube heat exchangers 11, 12.
  • the upper tubular heat exchanger 11 is carried by a holding frame 13 which is mounted on the side frame cheeks 14, 15 of the oven module 6. Together with an upper retaining plate 16 and a lower retaining plate 17, the two frame cheeks 14, 15 form a baking room module 18 in which, among other things, the two tubular heat exchangers 11, 12 of the baking oven module 2 i are accommodated.
  • An air guide plate 18a is arranged between the upper retaining plate 16 and the upper tubular heat exchanger 11. The latter serves to equalize a circulating air flow in the baking chamber 10.
  • the air guide plate 18a can also absorb heat energy from the tubular heat exchanger 11 and release it to the circulating air, so it can serve as an additional indirect heat exchanger component.
  • a corresponding air guide plate 18a is arranged between the lower tubular heat exchanger 12 and the lower holding plate 17.
  • An upper conveyor strand 19 of an endless conveyor belt 20 runs between the two tubular heat exchangers 11, 12 and is used to transport the baked goods through the respective continuous baking chamber 7, 8 between the loading module 4 and the output module 5.
  • the continuous oven 1 has two endless conveyor belts 20, namely an upper endless conveyor belt 20 for the oven modules 2 i and a similarly constructed lower endless conveyor belt for the lower oven modules 3 i . It is therefore sufficient to describe one of these conveyor belts below.
  • the conveyor belt 20 has a plurality of belt links 21, of which in the Fig. 2 an upper belt link 21 o and a lower belt link 21 u can be seen.
  • the upper belt link 210 is part of the upper conveyor strand 19 and is arranged in the baking chamber 10.
  • the lower belt link 21 u is part of a lower belt run 22 which runs beneath the baking chamber 10 and the lower tubular heat exchanger 11 through a return conveyor belt chamber 23 counter to the conveying direction 9 as part of the endless conveyor belt 20.
  • An upper air circulation duct 24 is arranged between the upper holding plate 16 of the baking room module 18 and an upper module plate 23a of the oven module 2 i , 3 i.
  • a lower circulating air duct 26 is arranged between the lower holding plate 17 of the baking room module 18 and a lower module plate 25.
  • the two circulating air ducts 24, 26 extend over the entire width of the oven module 2 i , 3 i .
  • the two circulating air ducts 24, 26 are in fluid connection with two axial / radial fans 31, 32 via supply and exhaust air ducts 27, 28, 29, 30. Overall, this results in a circulating air circuit of the respective oven module 2 i , 3 i .
  • the baking chamber 10 of the respective oven module 2 i , 3 i is part of this circulating air circuit.
  • the fans 31 and 32, together with the respective circulating air circuit, are components of a circulating air device of the continuous oven 1.
  • the two fans 31, 32 and the supply air and exhaust air ducts 27 to 30 are mounted on lateral, vertically extending frame plates 33, 34 of the oven module 2 i , 3 i .
  • Fig. 3 shows one of the two tube heat exchangers that are used in the oven module 2 1 using the example of the upper coil tube heat exchanger 11. All tubular heat exchangers 11, 12 of the oven modules 2 i , 3 i of the oven 1 are constructed in the same way, so that it is sufficient to describe this upper tubular heat exchanger 11 below.
  • the tubular heat exchanger 11 has a plurality, namely thirty-six in the illustrated embodiment, in an arrangement level (cf. level 35 in FIG Fig. 2 ) juxtaposed heat exchanger pipe sections 36 for guiding a heat transfer fluid.
  • Thermal oil in particular, can be used as the heat transfer fluid.
  • the arrangement of the heat exchanger tube sections 36 next to one another in the arrangement plane 35 can be such that actually in a side view as in FIG Fig. 2 all heat exchanger pipe sections 36 are completely aligned with one another.
  • longitudinal axes, in particular of adjacent pipe sections 36 can have different distances from the arrangement plane 35.
  • a bandwidth of the distances between the longitudinal axes of the pipe sections 36 and the arrangement plane 35 is, however, also in this case smaller than a diameter of the individual pipe sections 36 and is in particular smaller than a fraction of this diameter, for example less than 80%, less than 70%, less than 60%, less than 50%, less than 40%, less than 30%, less than 20% and in particular can be less than 10% of the The diameter of the pipe sections 36.
  • the pipe diameter of the pipe sections 36 can be in the range between 10 mm and 150 mm and, for example, in the range between 25 mm and 50 mm, for example 35 mm, 38 mm or 40 mm. Unless the pipe sections 36 in side view, as for example in the Fig. 2 are completely aligned with one another, the longitudinal axes of the pipe sections 36 can in this case have a distance from the arrangement plane 35 that is in the range between 0 mm and +/- 20 mm.
  • a distance A between two adjacent pipe sections 36 is on the one hand smaller than the pipe diameter and on the other hand greater than 1% of the pipe diameter.
  • This distance A is in the Fig. 6 , which shows a section of the tube heat exchanger 11 in a plan view, exemplifies two adjacent tube sections 36.
  • An absolute distance between two adjacent pipe sections 36 can be in the range between 1 mm and 50 mm, in particular in the range between 1 mm and 10 mm, in the range between 1 mm and 5 mm and can be, for example, 2 mm.
  • This distance between the adjacent pipe sections 36 enables a passage between these pipe sections.
  • Such a passage runs along an entire extension of the pipe sections 36 through the baking chamber 10 transversely to the conveying direction 9 and is at most interrupted by mounting components. Such interruptions are very small compared to the overall extent of the pipe sections 36 and Usually less than 5% of the total extension of the pipe sections 36. Because of these passages resulting from the distance between adjacent pipe sections 36, an effective heat transfer results from the pipe sections 36 to fluid flowing through between adjacent pipe sections 36.
  • FIG Fig. 7 Corresponding heat transfer conditions are very schematically shown in FIG Fig. 7 for two adjacent pipe sections 36 of the pipe heat exchanger 12.
  • the Fig. 7 shows the flow conditions at the lower coil pipe heat exchanger 12.
  • the heat transfer fluid 37 flows through the pipe sections 36.
  • the jacket walls 38 of the pipe sections 36 have a further heat-absorbing fluid, in the embodiment described, air 39 flowing around them, as shown schematically by some flow arrows reproduced. Due to the distance A between the adjacent pipe sections 36, which is in the range between 1% and 100% of the pipe diameter D, the inflowing air 39 flows through between the adjacent pipe sections after it has come into contact with peripheral sections U of the jacket walls 38.
  • the air 39 breaks off from the jacket wall 37 in the further course of the flow and the air 39 continues to flow turbulently upwards, where the Air which has flowed through the passage under consideration between the adjacent pipe sections 36 is effectively mixed with the air 39 which has flowed through adjacent passages between the pipe sections 36 shown and adjacent pipe sections not shown on the left and right.
  • a closed and essentially uninterrupted flow occurs very quickly Volume air flow upwards to the baking chamber 10, which is in the Fig. 2 is shown by flow arrows 40.
  • the turbulence ensures that the pipe sections 36 themselves do not serve as screens for the further air flow, that is, the air flow above the pipe heat exchanger 12 results in a closed air curtain without gaps through the baking chamber 10.
  • the tube heat exchanger 11 is designed as a coil tube heat exchanger.
  • a first serpentine conduit path 41 runs between a first serpentine conduit inlet 42 and a first serpentine conduit outlet 43.
  • a second serpentine conduit path 44 runs between a second serpentine conduit inlet 45 and a second serpentine conduit outlet 46 Fig. 3
  • the tubular heat exchanger 11 shown has exactly two serpentine line paths 41 and 44. In principle, a larger number of corresponding serpentine line paths is also possible.
  • the two serpentine line inlets 42, 45 on the one hand and the two serpentine line outlets 43 and 46 on the other hand are each in fluid connection via a Y-pipe section 49, 50 with one another and with a collecting inlet 49a on the one hand and with a collecting outlet 50a on the other hand.
  • the two serpentine line inlets 42, 45 are in fluid connection with the collecting line inlet 49a via the Y-pipe section 49.
  • the collecting line inlet 49a is in turn in fluid connection with a heat transfer fluid source not shown in the drawing.
  • the two collecting line outlets 43, 46 are in fluid connection with the collecting line outlet 50a via the further Y-pipe section 50.
  • the collecting line outlet 50a can be in fluid connection with the collecting line inlet 49a to form a heat transfer medium-fluid circuit.
  • a pump for the heat transfer fluid 37 which is likewise not shown in the drawing, can be part of this circuit.
  • the 180 ° deflection sections 47 are led out of the arrangement plane 35 between the two pipe sections 36 connected via this, namely bent out at an obtuse angle.
  • a bending angle ⁇ between the plane of arrangement 35 and a plane of arrangement of the 180 ° deflection sections 47 (cf. Fig. 2 , shown there in the tubular heat exchanger 12) is about 150 ° in the embodiment shown. This bending angle can be in the range between 120 ° and 165 °.
  • This routing of the 180 ° deflection sections 47 out of the arrangement plane 35 means that no installation space conflict occurs between the 180 ° deflection sections 47, 48 of the various hose line paths 41, 44.
  • a hose-pipe heat exchanger in the manner of hose-pipe heat exchangers 11 and 12 of the oven module 6 is produced as follows: First, a tube is provided which is a multiple of the length of one of the tube sections 36 between the respective deflection sections 47, 48. A first hose line path, for example the hose line path 41, is then produced by bending the pipe in the area of the deflection sections 47 between the pipe sections 36. A second hose line path, in this case the hose line path 44, is then produced by bending the pipe of the deflection sections 48 between the pipe sections 36. As soon as these manufacturing bending steps If the end of the tube is reached, a further tube with the same diameter is optionally pieced together, that is to say connected to the tube that has just been machined, for example welded to the end face.
  • the two hose line paths 41, 44 are inserted into one another in the arrangement plane 35.
  • the Y-pipe pieces 49, 50 can then be connected to the serpentine line inlets 42, 45 and the serpentine line outlets 43, 46, for example welded to them and optionally a fluid passage between the respective Y-pipe piece 49, 50 and the respective line inlets 42, 45 on the one hand and Outlets 43, 46 on the other hand are created.
  • the 180 ° deflection sections 47 between the pipe sections 36 of the same hose line path 41 are bent out of the arrangement plane 35. This bending out can take place at the same time when producing this serpentine conduction path 41 by using a corresponding, in particular flat, bending tool.
  • the baked goods carried on the conveyor belt 19 through the oven modules 2 to 6 are heated on the one hand by radiant heat from the tube heat exchangers 11, 12, which are housed in the respective oven modules 2 to 6, and on the other hand via the circulating air , which flows through the respective baking chamber 10 of the oven module 2 to 6, heated.
  • the heat contributions "radiant heat” on the one hand and “circulating air heat” (heat transfer to fluid flowing through) on the other can be specified by appropriate design of the tubular heat exchangers 11, 12 and by the temperature and flow of the heat transfer fluid 37 through the tubular heat exchangers 11, 12 and on the other hand by the amount of air flowing through the baking chambers 10.
  • An air flow through the baking chamber 10 (cf., for example, the air flow 40 in FIG Fig. 2 ) can be directed from bottom to top or from top to bottom, depending on the design of the furnace module 2 to 6.
  • Fig. 2 takes care of in the Fig. 2 Left fan 31 ensures that the circulating air first flows through the supply air duct 27 into the lower circulating air duct 26.
  • the Fig. 2 Right fan 32 ensures that the circulating air flows through the right supply air duct 28 into the lower circulating air duct 26.
  • the circulating air flows out of the lower circulating air duct 26 upwards and between the adjacent pipe sections 36 of the lower pipe heat exchanger 12, as above in connection with FIG Fig. 6 already described.
  • the circulating air then flows through the upper conveyor strand 19 of the endless conveyor belt 20 and then flows around the dough pieces conveyed thereon through the baking chamber 10.
  • the circulating air then flows through the passages between the pipe sections 36 of the upper tubular heat exchanger 11 and then flows into the upper circulating air duct 24, from where the circulating air is then sucked out again via the fans 31, 32 and the exhaust air ducts 29, 30 to complete the respective circulating air circuit.
  • An overpressure in the circulating air circuit can be achieved via a flap-controlled exhaust pipe 51 (cf. Fig. 2 ) escape.
  • the oven module can have 2 fans as in the version Fig. 2 or just an axial-radial fan have, which can then be attached to one or the other side of the furnace module.
  • the arrangement of this fan can alternate between the two sides of the continuous oven 1, for example, so that, for example, in oven module 3, the fan is arranged on the right in the manner of fan 32 following furnace module 4 on the left and in the following furnace module 5 again on the right.
  • the direction of flow of the circulating air through the baking chamber 10 can be specified by appropriately activating the respective fan 31, 32 from bottom to top or from top to bottom.
  • Different temperature zones can be specified in the furnace modules 2 to 6. This can be specified by specifying the temperature and / or the flow rate of the thermal oil and / or the amount of circulating air and the direction of the air circulation from bottom to top / from top to bottom. A central control device of the oven 1 is used for this.
  • the belt link 21 extends transversely to the conveying direction 9 between lateral guides 53, 54 for the endless conveyor belt 20, which are accommodated in the baking room module 18 for the upper conveyor strand 19.
  • the respective belt link 21 is connected to these guides 53, 54 via suspension mounting plates 55.
  • the upper conveying strand 19 extends in a conveying plane 56 which runs parallel to the planes of arrangement of the tubular heat exchangers 11, 12 (cf. plane of arrangement 35).
  • the band member 21 In projection in a direction perpendicular to the conveying plane 56, that is, seen in the viewing direction of FIG Fig. 9 , the band member 21 has gas passage openings 57, 58. These gas passage openings 57, 58 have a total opening area which is at least 30% of a total area of the projection of the band member 21.
  • the belt link 21 has between the lateral guides, that is, between the two suspension mounting plates 55, several link planes 59, 60 which, in the embodiment 2 shown, are spaced apart from one another perpendicular to the conveying plane 56.
  • the first, upper link level 59 coincides with the conveying level 56 and is defined by a plurality of double link brackets 63 extending along the conveying direction 9 between lateral link cheeks 61, 62.
  • the gas passage openings 58 are between the brackets of the respective double Link bracket 63 executed. Further gas passage openings in the upper link level 59 are made between two adjacent double link brackets 63.
  • the second, lower link level 60 is formed below the first link level 59 in the case of the belt links 21 currently forming the upper conveyor strand 19.
  • the gas passage openings 57 in the stiffening plate 64 run in the manner of elongated holes.
  • the gas passage openings 57 have a longitudinal extension in the direction of the longitudinal extension of the belt link 21.
  • the gas passage openings 58 between the brackets of the respective double link bracket 63 are designed in the manner of elongated holes.
  • the gas passage openings 58 have a longitudinal extension transverse to the longitudinal extension of the belt link 21, that is, as long as the belt link 21 is part of the upper conveying strand 19, parallel to the conveying direction 9.
  • the belt link 21 is designed to be self-supporting.
  • the belt links 21 revolve endlessly in the manner of chain links between the guides 53, 54, the upper conveyor strand 19 running in the conveying direction 9 and the lower belt strand 22 opposite to the conveying direction 9 Oven module 2 1 and the final oven module 2 N , a 180 ° deflection takes place via the correspondingly designed guides 53, 54 between the upper conveyor run 19 and the lower belt run 22.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Baking, Grill, Roasting (AREA)
EP19176648.4A 2018-06-06 2019-05-27 Rohrwärmetauscher für einen backofen Active EP3578911B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL19176648T PL3578911T3 (pl) 2018-06-06 2019-05-27 Rurowy wymiennik ciepła do pieca piekarniczego

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102018208952.3A DE102018208952A1 (de) 2018-06-06 2018-06-06 Rohrwärmetauscher für einen Backofen

Publications (2)

Publication Number Publication Date
EP3578911A1 EP3578911A1 (de) 2019-12-11
EP3578911B1 true EP3578911B1 (de) 2021-04-07

Family

ID=66655183

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19176648.4A Active EP3578911B1 (de) 2018-06-06 2019-05-27 Rohrwärmetauscher für einen backofen

Country Status (7)

Country Link
US (1) US11015881B2 (pl)
EP (1) EP3578911B1 (pl)
BR (1) BR102019011650A2 (pl)
DE (1) DE102018208952A1 (pl)
ES (1) ES2879425T3 (pl)
PL (1) PL3578911T3 (pl)
RU (1) RU2019115317A (pl)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102019212937B3 (de) * 2019-08-28 2020-08-13 Werner & Pfleiderer Industrielle Backtechnik Gmbh Durchlauf-Backofen für den kontinuierlichen Backbetrieb

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT27736B (de) 1905-10-12 1907-03-11 Hitz Fa J Verfahren zur Herstellung von Raupenleim.
GB191416746A (en) * 1914-07-14 1915-07-01 Waerme Verwertungs Ges Mit Bes Improvements in Heat-exchanging Apparatus.
DE927861C (de) * 1951-06-24 1955-05-20 August Lemke Backoefen, insbesondere mit einem oder mehreren Einschiess- oder Auszugherden
AU524322B2 (en) * 1978-05-29 1982-09-09 South African Coal, Oil + Gas Corp. Ltd. + Gea G.m.b.H. Air cooled heat exchanger for cooling industrial liquids
FR2555723B1 (fr) 1983-11-25 1988-02-05 Stein Industrie Dispositif de solidarisation de troncons verticaux adjacents rapproches de tubes d'un echangeur de chaleur a boucles
US20040069470A1 (en) * 2002-09-10 2004-04-15 Jacob Gorbulsky Bent-tube heat exchanger
WO2008086489A2 (en) * 2007-01-10 2008-07-17 Karamanos John C Embedded heat exchanger for heating, ventilation, and air conditioning (hvac) systems and methods
CH709194A2 (de) * 2014-01-17 2015-07-31 Joulia Ag Wärmetauscher für eine Dusche oder Badewanne.

Non-Patent Citations (1)

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

Also Published As

Publication number Publication date
BR102019011650A2 (pt) 2019-12-24
US20190376751A1 (en) 2019-12-12
EP3578911A1 (de) 2019-12-11
PL3578911T3 (pl) 2021-10-25
RU2019115317A (ru) 2020-11-20
US11015881B2 (en) 2021-05-25
DE102018208952A1 (de) 2019-12-12
ES2879425T3 (es) 2021-11-22

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