EP2149770A2 - Caloporteur tubulaire et procédé de transmission de la chaleur entre au moins deux flux d'aliments - Google Patents

Caloporteur tubulaire et procédé de transmission de la chaleur entre au moins deux flux d'aliments Download PDF

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Publication number
EP2149770A2
EP2149770A2 EP09009293A EP09009293A EP2149770A2 EP 2149770 A2 EP2149770 A2 EP 2149770A2 EP 09009293 A EP09009293 A EP 09009293A EP 09009293 A EP09009293 A EP 09009293A EP 2149770 A2 EP2149770 A2 EP 2149770A2
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EP
European Patent Office
Prior art keywords
heat transfer
heat exchanger
tube
deformed
transfer tubes
Prior art date
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Granted
Application number
EP09009293A
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German (de)
English (en)
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EP2149770A3 (fr
EP2149770B1 (fr
EP2149770B2 (fr
EP2149770A8 (fr
Inventor
Meinzinger Rupert
Johann Justl
Martin Zierer
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Krones AG
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Krones AG
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Publication of EP2149770A3 publication Critical patent/EP2149770A3/fr
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Publication of EP2149770B1 publication Critical patent/EP2149770B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D7/16—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
    • 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
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/006—Tubular elements; Assemblies of tubular elements with variable shape, e.g. with modified tube ends, with different geometrical features
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/08—Tubular elements crimped or corrugated in longitudinal section
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F13/00—Arrangements for modifying heat-transfer, e.g. increasing, decreasing
    • F28F13/06—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media
    • F28F13/08—Arrangements for modifying heat-transfer, e.g. increasing, decreasing by affecting the pattern of flow of the heat-exchange media by varying the cross-section of the flow channels
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
    • F28F9/007—Auxiliary supports for elements
    • F28F9/013—Auxiliary supports for elements for tubes or tube-assemblies
    • 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
    • F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
    • F28D2021/0042—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for foodstuffs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F2240/00—Spacing means

Definitions

  • the invention relates to a tubular heat exchanger for heat transfer between at least two food streams according to the preamble of claim 1 and a method for heat transfer between at least two food streams according to the preamble of claim 17.
  • heat transfer medium In the food industry, it is often necessary to extract or supply heat to a liquid food.
  • plate or tube heat exchangers are used.
  • a heating or cooling medium or heat storage or heat transfer medium is often used, which is used for the delivery and / or absorption of heat.
  • this heat transfer medium can then be used for a further heat transfer at another point in the production process.
  • the heat transferred beforehand from the heat transfer medium to the liquid food can be withdrawn by transferring it back to the transfer medium.
  • a heat transfer medium is disadvantageous in that a further heat transfer device may be required in a continuous manufacturing process.
  • a further heat transfer device may be required in a continuous manufacturing process.
  • the use of a heat carrier due to required additional equipment, such as tanks, Pipes and pumps, be complex and costly.
  • energy losses for example due to heat radiation and flow resistance, can be expected.
  • tubular heat exchangers have been proposed in which heat is transferred from a first food stream or from a first liquid product directly to a second food stream or a second liquid product without using a transmission medium.
  • This requires that even in a jacket space, which is formed between the jacket tube and usually a plurality of heat transfer tubes, a liquid product flows.
  • a heat transfer medium flows through the jacket space.
  • the jacket space must not only be fluidly designed for a liquid product, but must also be easy to clean.
  • baffles increase the flow resistance of the shell space and on the other hand can represent collection points for possibly contained in the liquid product solids. This can lead to an increased accumulation of suspended solids and / or to a burning of suspended or dissolved solids from the liquid product, the so-called fouling. Weaker heat transfer performance and more frequent cleaning intervals are the result.
  • the disadvantage here is that the applied axial force causes a permanent tension of the heat transfer tubes. This can lead to increased material stress and a shorter life of the heat exchanger.
  • the axial force must be generated by the use of additional components such as screws or spring sets. This complicates the installation of the tubular heat exchanger and also increases the manufacturing cost.
  • the invention is therefore based on the object, a generic tubular heat exchanger for heat transfer between at least two food streams or a generic method for heat transfer between at least two food streams in such a way that the heat transfer tubes are stored without bias using an axial force.
  • tubular heat exchanger for heat transfer between at least two food streams with the features of claim 1 and the method for heat transfer between at least two food streams with the features of claim 17.
  • a tubular heat exchanger wherein the tubular heat exchanger has a jacket tube and one or more heat transfer tubes are arranged in the interior of the jacket tube.
  • a first food stream or a first liquid food feasible in the at least one heat transfer tube.
  • a jacket space between the jacket tube and the at least one heat transfer tube second food stream or a second liquid food feasible.
  • at least a portion of the heat transfer tubes is at least partially deformed such that the spaced apart and adjacently arranged heat transfer tubes substantially only touch selectively.
  • sagging is avoided for the first time by an at least partial deformation of the heat transfer tubes, through which the heat transfer tubes spaced apart from one another and adjacent to one another touch each other only at certain points.
  • a storage of the heat transfer tubes is provided in a tubular heat exchanger, in which a sagging of the heat transfer tubes within the shell space is effectively avoided without biasing the heat transfer tubes.
  • the only substantially punctiform or punctiform or pointwise formed contact points between adjacent heat transfer tubes form a minimum flow resistance compared to all conventional installations for supporting the heat transfer tubes in the shell space of the tubular heat exchanger.
  • lower pumping capacities are required and the energy input into the liquid is reduced. This lowers Energy consumption and avoid unnecessary and possibly unwanted heating of the flowing food.
  • the substantially point-shaped contact points that have the advantage that, due to the design, an accumulation of solids contained in the liquid food is greatly reduced or even prevented. Accordingly, the product-contacted inner surfaces of the tubular heat exchanger remain free of deposits for longer, so that the heat transfer capability can be maintained at a high level for a longer time. This in turn results in high volume throughputs and long service life of the transmitter. This also involves less frequent cleaning intervals, which in turn allows for improved utilization.
  • the solution according to the invention offers an optimal construction, since the fixing of germs and other organisms as far as possible with respect to fixtures of any kind in the shell space. This in turn can be effectively counteracted the proliferation of product-harmful germs and the formation of difficult to remove biofilms.
  • the microbiologically improved conditions ultimately serve to maintain optimum product quality.
  • the heat transfer tubes arranged adjacent to the jacket tube and spaced therefrom can contact the jacket tube only selectively. According to the invention, it is thus provided for the first time to realize the support of the at least one heat transfer tube with respect to the casing-like casing tube by means of essentially point contact points. This results in the above-explained advantages in terms of flow resistance and cleanability analog.
  • the at least one heat transfer tube may have at least one deformed section with a changed cross-sectional shape.
  • the flow direction of the liquid is changed, which can lead to a better mixing.
  • turbulence which reduce the laminar boundary layer and thus improve heat transfer from the liquid to the wall.
  • the turbulences may have a cleaning effect on the addition of solids from the liquid food.
  • the transition from an undeformed section to the deformed section is continuous.
  • a steady transition minimizes flow resistance with the advantages discussed above.
  • the deformed portion may have a substantially elliptical cross section. This allows the realization of at least a point-trained contact point in a structurally simple manner. In addition, a high mechanical stability of the heat transfer tube is given at the deformed portion.
  • the deformed portion may also have a substantially circular cross-section with a diameter larger than the diameter of the heat transfer tube. This makes it possible to realize at least one punctiform contact point in a structurally even simpler way. In addition, it is advantageously possible to create more than two points of contact with other heat transfer tubes, whereby the supporting effect is improved. Before and / or after this enlarged diameter section, the deformed section may also have at least one reduced diameter section. This will be the Turbulence generation for the purpose of improved cleaning advantageously promoted, as discussed above.
  • the length of a main axis or the diameter of the deformed portion of the heat transfer tube is one to two times the diameter of the undeformed portion.
  • the spacing of the heat transfer tubes with each other can be preset in a simple manner. On the one hand, this enables a compact design of the tube heat exchanger and, on the other hand, allows the setting for the heat transfer of optimal flow conditions.
  • the undeformed portions and the deformed portions are alternately arranged one behind the other along a center axis of the heat transfer tube. This ensures that each heat transfer tube is taught only the required number of deformations, whereby the manufacturing process is simplified. Due to the minimum number of deformations and thus the contact points of the heat transfer tubes also the pressure loss of the flowing food is kept at a minimum possible value.
  • the substantially punctiform points of contact of the deformed portions may be spaced along the central axis of the heat transfer tube at a distance of about 0.1 to 3 meters, preferably about 1 to 2 meters.
  • a sufficient mutual support of the heat transfer tubes while avoiding sagging is possible.
  • the formation of natural vibrations of the tube bundle advantageously suppressed.
  • orientation of the major axes of two successive deformed sections having a substantially elliptical cross section may differ by a predetermined angle. This has the advantage that a support of two successive, deformed sections is aligned with at least two different, adjacent heat transfer tubes. This makes it possible to realize a support against all immediately surrounding tubes.
  • the predetermined angle between 0 and 180 °, preferably between 0 and 90 ° and in particular about 60 °. This allows sufficient support of a heat transfer tube with respect to all surrounding heat transfer tubes and the jacket tube.
  • the jacket tube can be deformed in its cross-section at least in sections such that it contacts the heat transfer tubes spaced apart from one another and arranged adjacent to one another substantially only at certain points. This improved support of the at least one heat transfer tube, the stability of the heat transfer tubes is additionally increased.
  • the substantially punctual points of contact of the jacket tube along a central axis of the jacket tube at a distance of about 0.1 to 3 m, preferably about 1 to 2 m from each other are arranged.
  • an improvement in stability is achieved with a minimal amount of deformation.
  • the cross-sectional shape of the heat transfer tubes may be malleable by section crimping.
  • the cross-sectional shape of the jacket tube can be formed by squeezing in sections.
  • the cross-sectional shape of the heat transfer tubes can also be formed by sectional forming by means of hydroforming or hydroforming and / or rolling and / or pressing. Hydroforming allows the production of deformed sections with rotationally symmetrical shape.
  • the object of the invention is achieved by the method according to the invention for heat transfer between two food streams.
  • the heat is transferred from a first food stream or a first liquid food to a second food stream or a second liquid food.
  • the first food stream is guided in at least one heat transfer tube of a tubular heat exchanger.
  • the second food stream is guided in a shell space of the tubular heat exchanger.
  • the jacket space is formed between a jacket tube and the at least one heat transfer tube.
  • at least a portion of the heat transfer tubes is at least partially deformed such that the spaced apart and adjacent arranged heat transfer tubes substantially only selectively touch.
  • the first food stream and the second food stream may contain different foods. Accordingly, the first and second foods may be two different foods. However, they can also be the same foods, in particular from different processing stages, in particular in recuperative stages.
  • the flow direction of the liquid food can change as it flows through the tubular heat exchanger at the deformed sections. As discussed above, this allows for greater Turbulences, a better mixing of the liquid food and thus an improved heat transfer.
  • FIGS. 1 to 5 shown detail of a heat transfer tube 1 has substantially the shape of a hollow cylinder. Furthermore, the illustrated section has at its ends two undeformed sections 2 with a substantially circular cross-section. In addition, the cutout in the central region has a deformed section 4.
  • the outer peripheral surface of the heat transfer tube 1 is flattened on two opposite sides, that is, at these points, the wall of the heat transfer tube 1 has a further curve than is the case with the undeformed sections 2.
  • the wall of the heat transfer tube 1 has a narrower curve than is the case with the undeformed portions 2.
  • the heat transfer tube 1 at the deformed portion 4 thus has a substantially elliptical cross-section.
  • the deformed portion 4 the diameter of the major axis of the substantially elliptical Cross section larger than that of the undeformed portion 2 of the heat transfer tube 1.
  • the minor axis of the substantially elliptical cross section is smaller than that of the undeformed portion. 2
  • Fig. 6 an exemplary embodiment of a bundle of cutouts of the heat transfer tubes 1 according to the invention is shown in perspective.
  • the heat transfer tubes 1 are arranged in the form of a bundle, wherein the center axes of the heat transfer tubes 1 are aligned parallel to each other.
  • the distance between two adjacent heat transfer tubes 1 is determined essentially by the length of the cross-sectional main axes of the deformed sections 4.
  • the diameter of the heat transfer tube 1 along the major axis of a deformed portion 4 is larger than that of the undeformed portion 2.
  • the heat transfer tube 1 has a plurality of above-described undeformed portions 2 and deformed portions 4 alternately arranged along the center axis of the heat transfer tube 1 in succession.
  • the deformed portions 4 along the central axis of the heat transfer tube 1 at a distance of about 1 m from each other.
  • the orientation of the main axes of two successive deformed sections 4 differs by a predetermined angle ⁇ of about 60 °.
  • every fourth of the deformed sections 4 has the same orientation of the main axis in space.
  • FIG. 3 illustrates a cross-sectional view of an exemplary embodiment of a tubular heat exchanger 6 according to the invention.
  • the tubular heat exchanger 6 according to the invention has a jacket tube 8, in the interior of which a bundle of heat transfer tubes 1 is arranged. Between the jacket tube 8 and the heat transfer tubes 1 is a jacket space 10th
  • the bundle of heat transfer tubes 1 is arranged such that each heat transfer tube 1, unless it is arranged adjacent to the jacket tube 8, is surrounded by six heat transfer tubes 1.
  • the heat transfer tubes 1, which are arranged adjacent to the jacket tube 8, are surrounded by three or four heat transfer tubes 1. With regard to the construction of the bundle of heat transfer tubes 1 is further on the description of the Fig. 6 directed.
  • a central heat transfer tube 1 whose central axis coincides with the center axis of the tubular heat exchanger 6 is surrounded by six heat transfer tubes 1. These are arranged in the form of an equilateral hexagon around the central heat transfer tube 1 and constitute a first sphere with respect to the central heat transfer tube 1.
  • the six surrounding heat transfer tubes 1 of the first sphere are further surrounded by 12 further heat transfer tubes 1.
  • These are again arranged in the form of an equilateral hexagon around the heat transfer tubes 1 of the first sphere and represent a second sphere with respect to the central heat transfer tube 1.
  • the tube heat exchanger 6 thus has 19 heat transfer tubes 1.
  • the deformed portions 4 of the heat transfer tubes 1 have a substantially elliptical cross section.
  • the main vertex of the deformed portions 4 each touch the outer peripheral surfaces of the undeformed portions 2 of the adjacently arranged heat transfer tubes 1.
  • 14 points of contact between the heat transfer tubes 1 are formed.
  • the points of contact are essentially of punctiform shape.
  • the jacket tube 8 also has in the in Fig. 7 Section shown six deformations of its substantially circular cross-section. These deformations have the shape of indentations, at the points of which the diameter of the jacket tube 8 is reduced.
  • the Deformations are arranged uniformly spaced on the circumferential line of the jacket tube 8. Further, they are each arranged in close proximity to the heat transfer tubes 1 of the second sphere with deformed cross sections. Due to the deformations, the jacket tube 8 has a circumferential line with a substantially wave-shaped form. The deformations are arranged along the central axis of the jacket tube 8 at a distance of 1 m from each other.
  • the deformations of the heat transfer tubes 1 and / or the jacket tube 8 have been generated by squeezing.
  • all the heat transfer tubes 1 have a deformed cross section.
  • the deformations of all heat transfer tubes 1, on a section axis through the tubular heat exchanger. 6 lie, the same spatial orientation of the respective main deformation axis. Of this deviates only the orientation of the main axis of the central heat transfer tube 1 from.
  • each heat transfer tube 1 has an overall undeformed cross section and two deformed cross sections.
  • the tubular heat exchanger 6 described above is used.
  • a liquid food flows through the heat transfer tubes 1, while another food flows through the jacket space 10.
  • the flow directions of the two foods may be the same or opposite.
  • the heat transfer takes place from the heat transfer tubes 1 through the wall to the shell space 10 or vice versa.
  • both the liquid food present in the heat transfer tubes 1 and the one located in the shell space 10 come into contact with the above-described deformations of the heat transfer tubes 1 and the jacket space 10. These deformations can too a change of the flow direction such that the mixing of the liquids is improved. As a result, a more uniform temperature distribution within the flowing liquids is achieved. This eventually leads to a larger temperature gradient on the wall, which limits the food streams, and thus to an improvement of the heat transfer.
  • FIG. 8 A detail of a further embodiment of the heat transfer tube 1 shown by way of example has substantially the shape of a hollow cylinder. Further for example, the illustrated section has at its ends two undeformed sections 2 with a substantially circular cross-section. In addition, the cutout in the central region has a deformed section 4.
  • the deformed section 4 has a rotationally symmetrical shape with a substantially circular diameter.
  • a section 12 of the deformed section 4 the diameter of the heat transfer tube 1 is increased relative to the undeformed sections 2, so that a kind of annular, circumferential cusp is formed.
  • the deformed section 4 in the immediate vicinity of the subsection 12 has at least one subsection 14 at which the diameter of the heat transfer tube 1 is reduced in relation to the undeformed sections 2, so that a type of constriction arises.
  • contour of the outer peripheral surface and the inner surface of the heat transfer tube 1 continuously changes from the undeformed portion 2 to the deformed portion 4.
  • FIG. 9 another exemplary embodiment of a tubular heat exchanger 6 according to the invention is shown in perspective.
  • the heat transfer tubes 1 are arranged in the form of a bundle, wherein the center axes of the heat transfer tubes 1 are aligned parallel to each other.
  • the heat transfer tubes 1 have the in the description of the figures Fig. 8 explained shape.
  • the distance between two adjacent heat transfer tubes 1 is determined essentially by the diameter of the deformed sections 4 and in particular by the diameter of the sections 12. Of the Diameter of the heat transfer tube 1 along the major axis of a deformed portion 4 is larger than that of the undeformed portion 2.
  • the outer peripheral surfaces of the deformed portions 4 and in particular those of the subsections 12 respectively contact the outer peripheral surfaces of the undeformed portions 2 of the adjacently arranged heat transfer tubes 1.
  • the points of contact are substantially of punctiform shape.
  • the bundle of heat transfer tubes 1 is surrounded by a jacket tube 8. Between the jacket tube 8 and the heat transfer tubes 1 is the jacket space 10.
  • the jacket tube 8 has a substantially circular diameter. However, the jacket tube 8 can also in Fig. 7 have described shape.
  • the heat transfer tube 1 has a plurality of above-described undeformed portions 2 and deformed portions 4 alternately arranged along the center axis of the heat transfer tube 1 in succession.
  • the deformed portions 4 along the central axis of the heat transfer tube 1 at a distance of about 1 m from each other.
  • the deformations of the heat transfer tubes 1 have been produced by hydroforming or any other suitable forming process.
  • liquids and in particular liquid foods or corresponding precursors can be used.
  • the tube heat exchanger 6 is provided for heat transfer between liquids such as water, beer, vegetable juice, fruit juice, lemonade, nectar, honey, milk, syrup, tea-based liquids, base, concentrates and any mixtures of these liquids, or the like.
  • liquids such as water, beer, vegetable juice, fruit juice, lemonade, nectar, honey, milk, syrup, tea-based liquids, base, concentrates and any mixtures of these liquids, or the like.
  • the abovementioned liquids may also contain solids, such as, for example, pulp, fruit pulp, fruit pieces, fibers, fiber, protein or the like.
  • the volume flows through the tubular heat exchanger according to the invention are 5 to 90 m 3 / h, preferably 7.5 to 60 m 3 / h and in particular 15 to 45 m 3 / h.
  • the temperature of the liquid food typically ranges from 0 to 150 ° C.
  • the temperature gradients of heat transfer are typically in the range of 2 to 15 ° C.
  • the inner diameter at an undeformed portion 2 of the heat transfer tube 1 is in the range of 10 to 100 mm.
  • the largest inner diameter or the length of the major axis at a deformed portion 4 of the heat transfer tube 1 is in the range of 11 to 120 mm.
  • the smallest inner diameter or the length of the minor axis at a deformed portion 4 of the heat transfer tube 1 is in the range of 5 to 50 mm.
  • the number of heat transfer tubes 1 can be 1 to 100 depending on the size be.
  • the distance between adjacently arranged heat transfer tubes 1 is in the range of 1 to 20 mm, in particular in the range of 2 to 10 mm. Further, the distance between the heat transfer tubes 1 and the jacket tube 8 is in the range of 1 to 20 mm.
  • the length of a heat transfer tube 1 is in the range of 2,000 to 6,000 mm.
  • the wall thickness of the heat transfer tube 1 is in the range of 1 to 6 mm.
  • the inner diameter of the jacket tube 8 is at an undeformed portion in the range of 15 to 500 mm, preferably in the range of 30 to 200 mm.
  • the largest inner diameter at a deformed portion of the mandrel 8 is in the range of 15 to 500 mm.
  • the smallest inner diameter at a deformed portion of the mandrel 8 is in the range of 13 to 470 mm.
  • the length of the jacket tube 8 is in the range of 2,000 to 6,000 mm.
  • the wall thickness of the jacket tube 8 is in the range of 1 to 6 mm.
  • the invention allows not only the illustrated embodiments but also further design approaches.
  • the undeformed portions 2 and / or deformed portions 4 of the heat transfer tube 1 may also have a cross section of a triangular or polygonal, elliptical, diamond-shaped, trapezoidal or other shape.
  • the deformed portions 4 may also have all the cross-sectional shapes, by squeezing, hydroforming, rolling, pressing or a otherwise reshaping the figures listed above are available.
  • the outer portions of the deformed portions 4 of the heat transfer tube 1, which are the contact points with another heat transfer tube 1 or the jacket tube 8, may instead be formed as a rounded peripheral surface also as a point-shaped tip or a tapered edge.
  • At least a part of the contact points between the heat transfer tubes 1 or between a heat transfer tube 1 and the jacket tube 8 may also be linear.
  • transition of the contour from the undeformed portion 2 to the deformed portion 4 need not be continuous.
  • the transition may also have edges or steps.
  • undeformed sections 2 and deformed sections 4 do not have to alternate. It is also conceivable that the deformed sections 4 merge into one another without having an undeformed section 2 arranged therebetween.
  • the deformed sections 4 can also be arranged at a distance of approximately 0.1 to 3 m, preferably approximately 1 to 2 m, from each other along the central axis of the heat transfer tube 1.
  • the predetermined angle ⁇ may also deviate from 60 ° and be 0 to about 180 °, preferably 0 to about 90 ° and in particular to 0 about 60 °.
  • the number of heat transfer tubes 1 of the first sphere surrounding the central heat transfer tube 1 is not limited to six. This number may be any integer between two and 12, preferably between four and ten, in particular between six and eight. Further, the number of heat transfer tubes 1 of the second sphere is not limited to 12. This number can be any integer between two and 39, preferably between seven and 19, in particular between ten and 14. Moreover, the tube heat exchanger 6 may also have three or more of the kind of the above-discussed spheres of heat transfer tubes 1. In addition, the type of arrangement of the heat transfer tubes 1 can be chosen arbitrarily.
  • the number of points of contact is not limited to 14. In particular, it can be varied as desired depending on the number of heat transfer tubes 1. Furthermore, it is conceivable that at least part of the contact points is formed by touching two or more deformed sections 4.
  • the number of deformations on the jacket tube 8 is not limited to six. It can be chosen arbitrarily, in particular depending on the diameter of the jacket tube 8 and the size of the deformations. In particular, an embodiment is conceivable in which the jacket tube 8 has no deformations.
  • the deformations of the jacket tube 8 may be of any shape. In particular, they may have the shape of a "bump". Furthermore, the Deformations not uniformly distributed on the circumferential line of the casing tube 8 may be arranged, but may be arranged at any distance from each other. In addition, the deformations along the central axis of the jacket tube at a distance of about 0.1 to 3 m, preferably about 1 to 2 m apart.
  • the jacket tube 8 may alternatively also have a cross-section of a triangular or polygonal, elliptical, diamond-shaped, trapezoidal or other shape.
  • the deformations of the heat transfer tubes 1 and / or the jacket tube 8 can be generated in addition to squeezing by any other mechanical or other method.
  • the fluid flowing through the jacket space 10 of the tubular heat exchanger 6 liquid is not limited to a liquid food.
  • any other liquid can be used, especially if it contains solids and / or tends to burn or fouling.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Instantaneous Water Boilers, Portable Hot-Water Supply Apparatuses, And Control Of Portable Hot-Water Supply Apparatuses (AREA)
EP09009293.3A 2008-08-01 2009-07-16 Utilisation d'un caloporteur tubulaire de transmission de la chaleur entre au moins deux flux d'aliments et procédé Not-in-force EP2149770B2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102008036125A DE102008036125A1 (de) 2008-08-01 2008-08-01 Röhrenwärmeüberträger und Verfahren zur Wärmeübertragung zwischen wenigstens zwei Lebensmittelströmen

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EP2149770A2 true EP2149770A2 (fr) 2010-02-03
EP2149770A3 EP2149770A3 (fr) 2011-03-23
EP2149770A8 EP2149770A8 (fr) 2011-06-22
EP2149770B1 EP2149770B1 (fr) 2013-02-27
EP2149770B2 EP2149770B2 (fr) 2016-11-23

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EP09009293.3A Not-in-force EP2149770B2 (fr) 2008-08-01 2009-07-16 Utilisation d'un caloporteur tubulaire de transmission de la chaleur entre au moins deux flux d'aliments et procédé

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EP (1) EP2149770B2 (fr)
CN (1) CN101639328B (fr)
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Cited By (5)

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Publication number Priority date Publication date Assignee Title
WO2014006151A1 (fr) 2012-07-05 2014-01-09 Tetra Laval Holdings & Finance S.A. Echangeur de chaleur tubulaire amélioré
WO2016120283A1 (fr) * 2015-01-26 2016-08-04 Valeo Systemes Thermiques Batterie thermique à matériau à changement de phase encapsulé
RU169811U1 (ru) * 2016-03-09 2017-04-03 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Брянский государственный технический университет" Трубчатый теплообменник
EP2984438B1 (fr) 2013-04-11 2018-12-26 SPX Flow Technology Danmark A/S Échangeur de chaleur hygiénique
WO2019202557A1 (fr) * 2018-04-19 2019-10-24 Koch Heat Transfer Company, Lp Appareil d'échange de chaleur et procédé de support de groupe de tubes à l'intérieur d'un échangeur de chaleur

Citations (1)

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DE60019635T2 (de) 1999-10-26 2006-03-02 Tetra Laval Holdings & Finance S.A. Rohrwärmetauscher-anordnung

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DE8704409U1 (fr) * 1987-03-25 1988-06-30 Schoenhammer, Johann, 8317 Mengkofen, De
DE3830800C1 (en) * 1988-09-09 1990-04-19 Proizvodstvennoe Ob"Edinenie "Nevskij Zavod" Imeni V.I. Lenina, Leningrad, Su Heat exchanger
DE9321031U1 (de) * 1993-12-18 1995-11-16 Friedrich Ambs Gmbh & Co Kg Ap Rohr, insbesondere zur Verwendung als Wärmetauschrohr für Rohrbündelwärmeübertrager
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DE60019635T2 (de) 1999-10-26 2006-03-02 Tetra Laval Holdings & Finance S.A. Rohrwärmetauscher-anordnung

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2014006151A1 (fr) 2012-07-05 2014-01-09 Tetra Laval Holdings & Finance S.A. Echangeur de chaleur tubulaire amélioré
EP2984438B1 (fr) 2013-04-11 2018-12-26 SPX Flow Technology Danmark A/S Échangeur de chaleur hygiénique
WO2016120283A1 (fr) * 2015-01-26 2016-08-04 Valeo Systemes Thermiques Batterie thermique à matériau à changement de phase encapsulé
US10746481B2 (en) 2015-01-26 2020-08-18 Valeo Systemes Thermiques Thermal battery with encapsulated phase-change material
RU169811U1 (ru) * 2016-03-09 2017-04-03 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Брянский государственный технический университет" Трубчатый теплообменник
WO2019202557A1 (fr) * 2018-04-19 2019-10-24 Koch Heat Transfer Company, Lp Appareil d'échange de chaleur et procédé de support de groupe de tubes à l'intérieur d'un échangeur de chaleur

Also Published As

Publication number Publication date
DE102008036125A1 (de) 2010-02-04
CN101639328B (zh) 2012-12-19
EP2149770A3 (fr) 2011-03-23
ES2400736T3 (es) 2013-04-11
EP2149770B1 (fr) 2013-02-27
CN101639328A (zh) 2010-02-03
EP2149770B2 (fr) 2016-11-23
EP2149770A8 (fr) 2011-06-22

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