EP1114975A2 - Echangeur de chaleur en spirale - Google Patents

Echangeur de chaleur en spirale Download PDF

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Publication number
EP1114975A2
EP1114975A2 EP00117298A EP00117298A EP1114975A2 EP 1114975 A2 EP1114975 A2 EP 1114975A2 EP 00117298 A EP00117298 A EP 00117298A EP 00117298 A EP00117298 A EP 00117298A EP 1114975 A2 EP1114975 A2 EP 1114975A2
Authority
EP
European Patent Office
Prior art keywords
spiral
heat exchanger
ribs
central
spiral heat
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.)
Withdrawn
Application number
EP00117298A
Other languages
German (de)
English (en)
Other versions
EP1114975A3 (fr
Inventor
Werner Dipl.-Ing. Borchert
Carsten Dipl.-Ing. Kühn
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.)
Kelvion Machine Cooling Systems GmbH
Original Assignee
Renzmann and Gruenewald GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Renzmann and Gruenewald GmbH filed Critical Renzmann and Gruenewald GmbH
Priority to JP2001000256A priority Critical patent/JP2001221581A/ja
Publication of EP1114975A2 publication Critical patent/EP1114975A2/fr
Priority to US10/016,657 priority patent/US20020092646A1/en
Publication of EP1114975A3 publication Critical patent/EP1114975A3/fr
Withdrawn legal-status Critical Current

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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
    • F28D7/04—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 spirally coiled
    • 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
    • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
    • F28D9/04—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being formed by spirally-wound plates or laminae
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/02—Tubular elements of cross-section which is non-circular
    • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels

Definitions

  • Spiral heat exchangers are technical devices that are relatively small Construction volume a high effective heat exchange between the same or allow different media.
  • spiral heat exchangers Another peculiarity of the known spiral heat exchangers are their relative high pressure drops. If these are to be reduced, however, the compactness limited.
  • This spiral heat exchanger is also designed as a so-called safety spiral heat exchanger with only one exceptionally high effort possible.
  • the object of the invention is based on the prior art to create a spiral heat exchanger that is avoiding of the disadvantages mentioned above is simple and, in particular in mass production for integration in automobiles with fuel cells, can be manufactured efficiently and inexpensively.
  • Such a spiral heat exchanger comprises at least two spiral elements, in which media of different temperatures flow. It can different media or identical media. Every spiral element is made up of a partially longitudinally slit central tube with at least a front media connection as well as one in the area of the longitudinal slot transversely attached to the central tube, spirally around the Central tube curved multi-channel profile together, the width of one Multiple times the height. The end section facing away from the central tube defines an overflow area for a medium. Each in heat exchange standing media enter a multi-channel profile through a central tube and flow in this up to the overflow area. This can be connected to the overflow area of another spiral element be axially attached to the first spiral element.
  • a spiral element can but also by an appropriate inner design one from the central tube to an overflow area and from this overflow area again complete flow path directed back to the central tube for a medium have.
  • a spiral heat exchanger designed in this way guarantees a perfect heat exchange between the Media in the intimately surrounding spiral elements.
  • the supply and discharge The media is only supplied via the core area of the spiral heat exchanger central tubes.
  • Each spiral element can have several spiral elements nested tightly one inside the other and, depending on the application, also carry more than two media.
  • the spiral heat exchanger is therefore extremely compact and can be used high exchange performance can be configured comparatively small volume. This makes the use in automobiles with fuel cells particularly advantageous.
  • the invention allows only the spiral elements to carry the media or additionally the areas between two nested ones Spiral elements are loaded with at least one medium.
  • the Areas between the spiral elements are then optionally over a multi-channel central feed pipe and also under Under certain circumstances, multi-channel central discharge pipe with feed and discharge lines connected.
  • the invention allows the radial width of the spiral elements can be designed differently, so that the throughput quantities can vary.
  • thermodynamic efficiency By dividing a single media stream into a larger number of spiral elements with a reduced radial width per media stream can also reduce the pressure drop while at the same time Improvement in thermodynamic efficiency can be effected.
  • the Spiral heat exchanger no complicated, especially spiral, To be welded.
  • the connections of the multi-channel profiles the central tubes are only through longitudinal seams, in particular through Welding ensured. Due to the multi-channel nature, the flow paths are short. This results in low temperature stresses.
  • it can be according to the invention may be advantageous two or more spiral heat exchangers to connect in series.
  • a performance adjustment be made during operation. So the entire facility for example when starting with a lower output and smaller ones Exchanger surfaces are operated. Only after reaching the full load situation all exchanger surfaces are switched on. Depending on the current The entire facility can then operate with the optimal efficiency. Also a shutdown a spiral heat exchanger or several spiral heat exchangers during an operation is quite possible.
  • the radially outer end sections defining overflow areas the spiral elements can be formed by deforming the multi-channel profiles his. Pipes of various cross-sections are also conceivable, however are attached to the front of the multi-channel profiles.
  • the different cross sections can be produced by deforming round tubes.
  • each medium can be in a single spiral element from the outside flow inwards and then from the inside out again or can two spiral elements can be axially placed in such a way that in one Spiral element the medium from the outside in, then over the overflow area flows into the neighboring spiral element and from there again flows from the inside out.
  • connections of the outer pipes that feed a medium on the one hand and the connections of the outer pipes that discharge a medium on the other hand are connected to each other in a media-conducting manner via ring channels.
  • the axial length is reduced.
  • the spiral elements according to claim 5 of be encased in a cylindrical housing.
  • the gap between the radially outer surfaces of the spiral elements and the inner wall of the housing is filled with a sealing material.
  • a sealing material can be a highly temperature-resistant Trade sealing material.
  • the spiral heat exchanger can at least in terms its spiral elements can be rotated about its longitudinal axis. This is e.g. then expedient if the spiral heat exchanger is used as an evaporator, for example of gasoline, as part of a so-called fuel cell to be used. It is to accelerate the evaporation effect then it makes sense to set the spiral heat exchanger in rotation. Because of the medium to be evaporated accelerates during rotation in the radial direction, associated with an increase in pressure, which in turn is synonymous with faster evaporation.
  • the spiral heat exchanger according to the invention When the spiral heat exchanger according to the invention is used as a compressor should be, especially if air is to be compressed, so becomes an acceleration due to the rotation of the entire spiral heat exchanger the air reaches in the radial direction. This is an increase pressure, which leads to faster compression of the air.
  • cold water is preferably used as the exchange medium to use.
  • the spiral heat exchanger according to the invention can stationary, i.e. operated at standstill as a pure heat exchanger become. But it is also conceivable with regard to e.g. faster and more intensive evaporation on the one hand and compression on the other perform rotary operation.
  • a compressor with an expansion device Coupled (turbine) designed spiral heat exchanger By doing In particular, air is compressed on its flow path by the compressor inner areas compressed to the radially outer areas. Of In the overflow areas, the compressed air becomes axially adjacent Spiral heat exchanger supplied radially from the outside and then attaches there again in the spiral elements from radially outside to radially inside Flow path back. At the same time, a coolant flows in the case of a turbine in the spiral elements, so in this way a turbocharger is created.
  • Another mode of operation of the spiral heat exchanger can be that heat exchange takes place between two media and at least one of these media is to be funded at the same time.
  • the features of claim 7 of particular Advantage are the features of claim 7 of particular Advantage.
  • the radially outer end portions of the Central pipes connected and in particular rotatable in a housing Spiral elements bent like a wing towards the inner wall of the housing. This creates quasi guiding surfaces.
  • heat exchange is effected on one side and on the other hand at least one of the media through the bent Guiding surfaces exposed to a pumping action and thus a certain one Goal promoted.
  • two radially adjacent, axially displaceable spiral elements one with Radial openings provided the size of the other spiral element are at least indirectly changeable. Then if the other spiral element still with spacers and these spacers with sliding feet be equipped that can slide over the radial openings, it is possible by an axial relative displacement of the two spiral elements, the Enlarge or reduce openings. In this way, in particular an advantageous mode of operation when condensing a medium be achieved.
  • the axial displaceability of at least two nested Spiral elements can also be used to create an intermediate to either condense the medium guided by the two spiral elements, wherein a cooling fluid flows in the spiral elements or it becomes between the fluid guided fluid relaxed or pumped, wherein then a higher temperature medium is guided in the spiral elements.
  • This design can be used independently whether the spiral heat exchanger is integrated in a housing or not.
  • a further advantageous embodiment of the invention is in the features characterized in claim 10. Then the central pipes point or the outer tubes of the spiral elements each have an inlet chamber and an outlet chamber, which through in the central tubes or in the outer tubes tightly inserted transverse walls are separated from each other.
  • This Design allows the respective one to be guided within a spiral element Medium from radially inside or radially outside to radially outside or radially inside and back again.
  • each transverse wall with a nose-like Projection between two the flat sides of the multi-channel profiles of the spiral elements spacing ribs that maintain a distance and form individual channels see above works especially when setting, preferably by welding, one Multi-channel profile on a central tube or on an outer tube of the projection as a centering welding gauge.
  • About the freely selectable height of the Spacer ribs can also be spiral elements with different volume throughput to be provided.
  • Overflow areas for the media can thereby according to claim 12 formed that the spacer ribs from the central tubes or extend the outer tubes up to the wedge-shaped end sections. In the wedge-shaped end sections are then no longer spacer ribs.
  • wire inserts according to the features of the claim 13 further improved. These wire inserts are used when the Multi-channel profiles inserted. They are in the range between two Spacer ribs, i.e. So in the channel area, so that then due to the resilient Preload between two spiral elements zones are created which, especially in so-called safety spiral heat exchangers, exercise their safety function.
  • Claim 15 be formed.
  • edges radially inner flat sides of the multi-channel profiles differ from the Central tubes or the outer tubes from up to the transverse edges of the end sections extending, tapering in the region of the end sections End ribs provided, and in the central longitudinal plane of the multi-channel profiles central ribs run from the central tubes or the outer tubes to the end sections.
  • Longitudinal ribs between the end ribs and the middle ribs All the ribs then act with the peripheral ribs of the adjacent spiral elements together.
  • Claim 16 be formed. After that is between the Circumferential ribs of the multi-channel profile of a spiral element on the one hand and the End ribs as well as the central rib of the multi-channel profile of the radially adjacent one Spiral element, on the other hand, integrates an insert sheet that itself from the common longitudinal axis of the spiral elements to approximately itself extends wedge-shaped tapered longitudinal sections of the circumferential ribs. An insert plate prevents the various ribs from sliding into one another. In addition, a center chicane should also be used in this embodiment to get integrated.
  • the multi-channel profiles can be divided into lengths extruded aluminum profiles.
  • the multi-channel profiles stretched there become wedge-shaped end sections then, for example, with an appropriately trained milling cutter from the Spacer ribs freed.
  • the flat sides are merged, until their front edges lie together. These front edges are after that tightly connected, especially welded.
  • the long edges of the Flat sides are sealed in the end sections, preferably welded.
  • the multi-channel profiles with circumferential ribs, end ribs, middle ribs and if necessary, longitudinal ribs can be according to the features of the claim 18 also made of extruded aluminum sections divided into lengths be educated.
  • the circumferential ribs as well the center ribs are removed in the area of the wedge-shaped end sections.
  • end portions adjacent to the peripheral ribs are chamfered in a wedge shape.
  • the length of these areas corresponds approximately to the length of the end sections.
  • the side ribs are led to the edges, however tapered in the area of the end sections.
  • the cuts and bevels can be created by milling.
  • the spacer ribs have already on the before welding Sheet steel strips a length equal to the length of a wedge-shaped end section is shorter.
  • the same situation applies to the embodiment with circumferential ribs, end ribs, central ribs and, if necessary, longitudinal ribs, which can be configured accordingly before welding.
  • the welding method can preferably be used with laser welding.
  • the spacer ribs To the in the steel sheet welded construction according to claim 19 to ensure bending of the spacer ribs over the vertical axis, it is after Claim 20 useful, the spacer ribs, especially on the radially inner longitudinal edges, preferably with wedge-shaped incisions to provide. These then close when winding. To this The spacer ribs do not become wise in the case of the spiral curvature Subjected to constraints. Need the radially outer longitudinal edges just to be slit.
  • 1 denotes a spiral heat exchanger, as it is e.g. used in automotive engineering in connection with fuel cells.
  • the spiral heat exchanger 1 comprises in a cylindrical housing 2 eight spiral elements 3 that can be seen in more detail in FIG. 2.
  • the spiral elements 3 are arranged offset to one another in the circumferential direction and axially one inside the other pushed (nested).
  • Each spiral element 3 consists of one based on FIGS. 3 and 4 explained central tube 4 and a spiral curved around the central tube 4 Multi-channel profile 5, which is also based on Figure 3 below is explained in more detail ( Figure 2).
  • the central tubes 4 of the spiral elements 3 are all on the same pitch circle 6 ( Figure 1).
  • transverse edges 7 of the spiral elements 3 facing away from the central tubes 4 are each on the surface 8 of the radially outer flat side 21 of the spiral element adjacent with respect to the central tube 4 in the direction of curvature 3 fixed by welding.
  • the spiral heat exchanger 1 has a front view according to FIG. 1 an essentially cylindrical contour.
  • the gap 10 between the radially outer surfaces 8 of the spiral elements 3 and the inner wall 11 the housing 2 is filled with a sealing material 12.
  • FIG. 3 and 4 is in each central tube 4 in a coaxial assignment an inlet chamber 13 for a medium A or B and an outlet chamber 14 trained.
  • the inlet chamber 13 and the outlet chamber 14 are separated by a transverse wall 15 with a nose-like projection 16 Cut.
  • the entry chamber 13 is connected via the end face 17 with e.g. applied to the medium A. Via the opposite end face 18 the medium A leaves the outlet chamber 14.
  • a multi-channel profile 5 is welded transversely.
  • Such one Multi-channel profile 5 can, according to the embodiment in FIG. 6, consist of one extruded aluminum profile divided to length. His Width B1 corresponds to a multiple of height H.
  • the two flat sides 21, 22 of the multi-channel profile 5 are laterally through longitudinal walls 23 and between the longitudinal walls 23 connected by spacer ribs 24. In this way, 5 individual channels 25 in two channel strands are in the multi-channel profile 45, 46 formed.
  • the individual channels 25 in the channel strand 45 are in the longitudinal slot 19 Central tube 4 with the inlet chamber 13 and in the duct 46 with the outlet chamber 14 in medium-conducting connection ( Figure 3).
  • the nose-like projection 16 formed on the transverse wall 15 is used for Welding the multi-channel profile 5 to the central tube 4 as a centering (Welding gauge) by reaching into a single channel 25.
  • the multi-channel profile 5 according to FIGS. 1 and 2 then becomes spiral curved.
  • a current filament STF of the medium A is the Flow through a spiral element 3 exemplified.
  • the medium A occurs over the End face 17 in the inlet chamber 13 and from here passes through the Longitudinal slot 19 in the channel strand 45 in the multi-channel profile 5, which with the Entry chamber 13 is connected.
  • the medium A flows through the channel line 45 and passes over the overflow area formed in the end section 9 ÜB in the channel line 46, which is connected to the outlet chamber 14 is.
  • the medium A then leaves the spiral element 3 via the end face 18 of the outlet chamber 14.
  • FIG. 5 shows a spiral element 3a in an extended position, at which the multi-channel profile 5a has a cross section as shown in FIG. 7 is shown.
  • a multichannel profile 5a extruded in this way and divided into lengths becomes processed with respect to the inner spacing ribs 24 exactly as with the Figure 3 explains.
  • the longitudinal sections lying in the area of the end section 9 35 of the lateral end ribs 30 are wedge-shaped here designed.
  • the central rib 31 is also in the region of the end section 9 away. Also the ends 47 of the circumferential ribs adjoining the central tube 4 29 beveled.
  • overflow areas are thus not only in the end sections 9 of the multi-channel profiles 5a ÜB formed for the respective media A, B, but by the Ribs 29, 30, 31 and optionally 32 also spiral channels in the Area 36 between two multi-channel profiles 5a.
  • These areas 36 act then as safety zones, for example in a safety spiral heat exchanger.
  • the regions 36 can optionally be combined with one, in particular neutral, fluid are applied.
  • FIG. 5 corresponds to that of the figure 3, so that there is no further explanation.
  • spiral elements 3a according to FIGS. 5 and 7 can thus be assigned to one another that the peripheral ribs 29 of a spiral element 3a with the terminating ribs 30, the central rib 31 and optionally the longitudinal ribs 32 of a radially adjacent spiral element 3a each in the same Cross planes run. It is also conceivable according to FIG.
  • Multi-channel profiles 5a of two adjacent spiral elements 3a in the axial direction of the spiral heat exchanger 1 are offset from one another such that the circumferential ribs 29 on the one multi-channel profile 5a are located radially on the inside Contact flat side 22 of the adjacent multi-channel profile 5a, while the finishing ribs 30, the central rib 31 and possibly the Longitudinal ribs 32 of the radially outer multichannel profile 5a are the radially outer ones Contact flat side 21 of the inner multi-channel profile 5a.
  • the central tube 4 remains unchanged.
  • the welded to the central tube 4 Multi-channel profile 5b of the spiral element 3b consists of a high temperature resistant welded sheet steel construction.
  • spacing ribs 24a are edged onto one another in the longitudinal direction Sheet steel strips 38 welded. Then this is with the spacer ribs 24a provided steel sheet strips 38 bent transversely to the multi-channel profile 5b and its longitudinal edges 39 then welded together.
  • this multi-channel profile 5b can easily spiral around a central tube 4 can be curved, are preferably the radially inner longitudinal edges 40 of the spacer ribs 24a are provided with wedge-shaped incisions 41.
  • the outer longitudinal edges 40 can also have such incisions 41 be provided.
  • FIG. 11 shows the embodiment of a in vertical partial cross section Spiral heat exchanger 1a with a total of four spiral elements 3a according to the embodiment of Figures 5 and 7.
  • the spiral heat exchanger 1a can have at least one a central baffle 48 in the form of a sheet, which in each area 44 a spiral flowing up and down Flow of a medium A or B guaranteed.
  • the areas 44 are then Via end piece 49 with feed and discharge lines that can be seen in FIG in connection.
  • FIG. 12 and 13 is an embodiment of a spiral heat exchanger in the diagram 1b recognizable, in which a Housing 2 seen two groups 50, 51 of two nested in each other Spiral elements 3c are provided.
  • the central tubes 4a of both Groups 50, 51 are separated from each other so that the central tubes 4a of the group 50 media supplied, in the radially outer overflow area Transfer from group 50 to group 51 and via the central tubes 4a of group 51 are removed again.
  • the flow of the Media is characterized by the STF current threads.
  • the design of the individual spiral elements 3c can correspond to the Embodiments described above take place.
  • the radially outer end portions 9 of the spiral elements 3c, which The overflow areas UB are defined by an approximately triangular deformation formed by circular tubes ( Figure 13).
  • the central tubes 4a are each with their end faces Connections 59, 60 connected to housings 61.
  • the housings 61 are then each with a tubular feed line 62 and a tubular one Lead 63 provided.
  • Walls 64, 65 are drawn in at the front of the housing 2.
  • the walls 64, 65 are channeled, which is due to the dash-dotted lines is illustrated.
  • the medium enters the wall 64 at 66 and reaches the wall from here 64 to the central area of the housing 2 and flows here in the group 50 radially outward between the spiral elements 3c.
  • the radially outer Area enters the medium according to the dash-dotted lines Streams STF over to group 51 and flows here between the Spiral elements 3c from the radially outer area to the radially inner area Area.
  • the medium then enters the channels of the wall 65 and flows in wall 65 radially outward and leaves housing 2 at 67.
  • a spiral heat exchanger 1c is shown in the diagram in FIG which both at the radially inner ends of the arranged in a housing 2 Spiral elements 3d as well as at the radially outer ends circular tubes 52, 53 are provided.
  • the lengths between the tubes 52 and 53 can according to Figures 3 or 5 to 13 be formed.
  • the spiral heat exchanger 1c can be of various types Operated in a manner.
  • the spiral heat exchanger 1c is to be operated as a direct current, so the media can enter the spiral elements 3d via the central tubes 52 and via the radially outer ones that define the overflow areas UB Pipes 53 are deflected.
  • the media in the spiral elements 3d can be different or identical.
  • the spiral heat exchanger 1c is operated so that the media over the radially outside lying tubes 53 enter the spiral elements 3d and over the radial central tubes 52, which then define the overflow areas be redirected.
  • the media can also be identical or different in this mode of operation his.
  • spiral heat exchanger shown in Figure 14 can 1c can be operated as a counterflow.
  • the media can be different or be identical.
  • the flow directions are in this case indicated with the STF current threads
  • a spiral heat exchanger 1d of the figures 15 and 16 illustrate that infeed and outfeed the media via the outer tubes 53 of the spiral elements 3d the outer tubes 53 are then connected to one another via ring channels 54, 55 located outside a housing 2 are connected to the media.
  • the spiral elements are 3d again divided into two groups 50, 51.
  • the spiral elements 3d of the group 50 are connected via their outer tubes 53 to the ring channel 54, while the spiral elements 3d of group 51 via their outer tubes 53 with the Ring channel 55 are connected.
  • the central tubes 52 of the spiral elements 3d are formed jointly for both groups 50 and 51, that is, here they form the overflow areas ÜB.
  • FIG. 17 shows an embodiment of a spiral heat exchanger 1e, in which the radially outer, defining the overflow areas ÜB End sections 9a of the connected to central tubes 4a and in a housing 2 to rotate about a longitudinal axis 43 spiral elements 3e Inner wall 11 of the housing 2 are bent wing-like. Arise then guiding surfaces. When the spiral elements 3e rotate about the longitudinal axis 43 can then generate heat exchange as well as through the bent end portions 9a a pumping effect can be achieved.
  • the media flow over the Central tubes 4a enter the spiral elements 3e of one group 50 from here to the wing-like bent end sections 9a transferred there to the other group 51, arrive from the end sections 9a to the other central tubes 4a and then leave the spiral heat exchanger 1e again.
  • FIGS. 18 and 19 show an embodiment of a spiral heat exchanger 1f, in which of at least two nested Spiral elements 3f, 3g one, e.g. 3f with openings 56 on the inside is provided.
  • the other spiral element 3g has spacers 57 with sliding feet 58 which can slide over the openings 56. At a axial Relativwerlagerung of the two spiral elements 3f, 3g can then the openings 56 are enlarged or reduced.
  • This variant of a spiral heat exchanger 1f is preferred in the Condensation of a medium used.
  • the flow of the media is approximately as follows: Since the spiral elements 3f, 3g are divided by a central baffle 48, the media pass from the central tubes 4a via the spiral elements 3f, 3g to the radially outer end sections 9, where they are then deflected and in the other partial area of the spiral elements 3f, 3g again flow out to the inner central tube 4a.

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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)
EP00117298A 2000-01-07 2000-08-18 Echangeur de chaleur en spirale Withdrawn EP1114975A3 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2001000256A JP2001221581A (ja) 2000-01-07 2001-01-04 螺線状熱交換器
US10/016,657 US20020092646A1 (en) 2000-01-07 2001-12-12 Spiral heat exchanger

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE2000100288 DE10000288C1 (de) 2000-01-07 2000-01-07 Spiralwärmeaustauscher
DE10000288 2000-01-07

Publications (2)

Publication Number Publication Date
EP1114975A2 true EP1114975A2 (fr) 2001-07-11
EP1114975A3 EP1114975A3 (fr) 2002-03-27

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EP00117298A Withdrawn EP1114975A3 (fr) 2000-01-07 2000-08-18 Echangeur de chaleur en spirale

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EP (1) EP1114975A3 (fr)
DE (1) DE10000288C1 (fr)

Cited By (3)

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Publication number Priority date Publication date Assignee Title
DE10215091A1 (de) * 2001-04-05 2002-11-14 Modine Mfg Co Spiralförmige Rippe/Röhre als Wärmeaustauscher
WO2016057471A1 (fr) * 2014-10-07 2016-04-14 Unison Industries, Llc Échangeur de chaleur enroulé en spirale à écoulements croisés
WO2024200504A1 (fr) * 2023-03-30 2024-10-03 Kaeser Kompressoren Se Échangeur de chaleur d'un séchoir à adsorption

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RU2557146C1 (ru) * 2014-09-22 2015-07-20 Андрей Владиславович Курочкин Радиально-спиральный теплообменник
RU2558664C1 (ru) * 2014-09-22 2015-08-10 Андрей Владиславович Курочкин Радиально-спиральный теплообменник
DE102017106175A1 (de) 2017-03-22 2018-09-27 Thyssenkrupp Ag Boden für eine Stoffaustauschkolonne
DE102017106177A1 (de) 2017-03-22 2018-09-27 Thyssenkrupp Ag Boden für eine Stoffaustauschkolonne
RU2640139C1 (ru) * 2017-04-11 2017-12-26 Андрей Владиславович Курочкин Радиально-трубный тепломассообменный аппарат

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Publication number Priority date Publication date Assignee Title
EP0380419A1 (fr) 1989-01-25 1990-08-01 SPIREC, Société à Responsabilité Limitée Echangeur de chaleur à corps enroulé en spirale et son procédé de fabrication
EP0529819A2 (fr) 1991-08-22 1993-03-03 Modine Manufacturing Company Echangeur de chaleur

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US3854530A (en) * 1969-12-29 1974-12-17 E Jouet Heat exchanger
DE3319521A1 (de) * 1983-05-28 1984-11-29 Kienzle Apparate Gmbh, 7730 Villingen-Schwenningen Waermeaustauscher fuer fluessige medien
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JPH031095A (ja) * 1989-05-29 1991-01-07 Nippon Stainless Steel Co Ltd 渦巻板型熱交換器及びその製造方法
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EP0380419A1 (fr) 1989-01-25 1990-08-01 SPIREC, Société à Responsabilité Limitée Echangeur de chaleur à corps enroulé en spirale et son procédé de fabrication
EP0529819A2 (fr) 1991-08-22 1993-03-03 Modine Manufacturing Company Echangeur de chaleur

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10215091A1 (de) * 2001-04-05 2002-11-14 Modine Mfg Co Spiralförmige Rippe/Röhre als Wärmeaustauscher
US6607027B2 (en) 2001-04-05 2003-08-19 Modine Manufacturing Company Spiral fin/tube heat exchanger
WO2016057471A1 (fr) * 2014-10-07 2016-04-14 Unison Industries, Llc Échangeur de chaleur enroulé en spirale à écoulements croisés
US10274265B2 (en) 2014-10-07 2019-04-30 Unison Industries, Llc Spiral wound cross-flow heat exchanger
WO2024200504A1 (fr) * 2023-03-30 2024-10-03 Kaeser Kompressoren Se Échangeur de chaleur d'un séchoir à adsorption

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EP1114975A3 (fr) 2002-03-27

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