EP2379978A2 - Appareil pour la répartition de fluides et leur échange de chaleur et/ou de matière - Google Patents

Appareil pour la répartition de fluides et leur échange de chaleur et/ou de matière

Info

Publication number
EP2379978A2
EP2379978A2 EP09795934A EP09795934A EP2379978A2 EP 2379978 A2 EP2379978 A2 EP 2379978A2 EP 09795934 A EP09795934 A EP 09795934A EP 09795934 A EP09795934 A EP 09795934A EP 2379978 A2 EP2379978 A2 EP 2379978A2
Authority
EP
European Patent Office
Prior art keywords
aperture
tube
fluid distributor
inner tube
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.)
Granted
Application number
EP09795934A
Other languages
German (de)
English (en)
Other versions
EP2379978B1 (fr
Inventor
Michael Hermann
Constanze Bongs
Hans-Martin Henning
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.)
Fraunhofer Gesellschaft zur Foerderung der Angewandten Forschung eV
Original Assignee
Fraunhofer Gesellschaft zur Foerderung der Angewandten Forschung eV
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 Fraunhofer Gesellschaft zur Foerderung der Angewandten Forschung eV filed Critical Fraunhofer Gesellschaft zur Foerderung der Angewandten Forschung eV
Priority to PL09795934T priority Critical patent/PL2379978T3/pl
Publication of EP2379978A2 publication Critical patent/EP2379978A2/fr
Application granted granted Critical
Publication of EP2379978B1 publication Critical patent/EP2379978B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B01—PHYSICAL OR CHEMICAL PROCESSES OR APPARATUS IN GENERAL
    • B01F—MIXING, e.g. DISSOLVING, EMULSIFYING OR DISPERSING
    • B01F25/00—Flow mixers; Mixers for falling materials, e.g. solid particles
    • B01F25/40—Static mixers
    • B01F25/42—Static mixers in which the mixing is affected by moving the components jointly in changing directions, e.g. in tubes provided with baffles or obstructions
    • B01F25/43—Mixing tubes, e.g. wherein the material is moved in a radial or partly reversed direction
    • B01F25/432—Mixing tubes, e.g. wherein the material is moved in a radial or partly reversed direction with means for dividing the material flow into separate sub-flows and for repositioning and recombining these sub-flows; Cross-mixing, e.g. conducting the outer layer of the material nearer to the axis of the tube or vice-versa
    • B01F25/4321—Mixing tubes, e.g. wherein the material is moved in a radial or partly reversed direction with means for dividing the material flow into separate sub-flows and for repositioning and recombining these sub-flows; Cross-mixing, e.g. conducting the outer layer of the material nearer to the axis of the tube or vice-versa the subflows consisting of at least two flat layers which are recombined, e.g. using means having restriction or expansion zones
    • 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
    • F28D9/0012—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 apparatus having an annular form
    • F28D9/0018—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 apparatus having an annular form without any annular circulation of the heat exchange media
    • 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
    • F28D2021/0052—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for mixers

Definitions

  • the present invention relates to a Fluidvertei- ller, a heat and / or material exchanger and an apparatus having at least one fluid distributor and arranged thereon a heat and / or material exchanger.
  • Apparatuses for exchanging heat and / or substances between different fluids are state of the art. These include, for example, plate heat exchangers in which numerous flat fluid channels are arranged parallel to one another and thus offer a large exchange surface. This design is widely used, especially in air-air heat exchangers, which are used for example for the recovery of warmed.
  • the channels are arranged alternately, that is to say in the sequence ABABAB.
  • each incision has a longitudinally extending from the first to the second aperture Trajek- tone which reduces the radius of the inner tube, starting from the original radius of the inner tube at the height of the first aperture longitudinally in the direction of the second aperture, wherein all trajectories of the Incisions at the height of the second aperture converge in the center of the cross-section of the fluid distributor, and each invagination has a longitudinally extending from the first to the second aperture trajectory, which increases the radius of the inner tube, starting from the original diameter of the inner tube at the height of the first aperture longitudinally in the direction of the second aperture, all trajektorien the protuberances at height the second aperture converge with the outer tube.
  • a rotationally symmetrical fluid distributor is understood to mean a device which always has a round (ie circular) cross-section, but the diameter in the longitudinal direction of the fluid distributor does not have to be constant, but can be constant.
  • the entire fluid distributor seen from the outside may have a cylindrical shape, but also have an increasing diameter, for example from the first to the second aperture.
  • the fluid distributor has at its two ends on the first aperture and the second aperture.
  • the fluid manifold consists essentially of two nested tubes, the inner tube enclosing a space A and the outer and inner tubes enclosing a space B, while the second aperture is segmented, with the respective segments alternating with the first Rooms A and B, so the spaces that are enclosed at the first aperture of the inner tube or of the two tubes, in conjunction.
  • the fluid distributor takes place between the first and second aperture, a transition in which the inner tube has increasing notches and protuberances, wherein the notches, ie the trajectory of the respective notches, in the longitudinal course of the first to the second aperture in the direction of the center of the
  • Fluid distributor and at the latest at the th aperture converge with the center of the fluid manifold.
  • the trajectory of the protuberances ie the radial course of the protuberances, runs in the longitudinal direction from the first to the second aperture in the direction of the outer tube, whereby at the latest at the second aperture the trajectory of the protuberances with the outer tube converges.
  • a fluid transition between the circular / annular spatial distribution towards a segment-like spatial distribution of the spaces A and B is provided with the fluid distributor.
  • the outer diameter of the entire fluid distributor can remain the same over the entire length of the distributor, but also vary.
  • Cross-sectional areas with respect to space A and space B remains constant over the entire length of the fluid distributor.
  • This preferred embodiment thus provides that at each point of the cross-section of the fluid distributor, the ratio of the area which originates from room A to the area which originates from room B, is the same.
  • the cross-sectional area of A / B at each point of the fluid distributor is therefore equal to 1 in cross-section.
  • the respective segments A and B at the second aperture are also inferential result in exactly the same areas.
  • the cross-sectional areas of the space A can be much larger than those of B and vice versa (e.g., 50: 1 or
  • the trajectories of the incisions and / or the protuberances run "sinusoidally."
  • the trajectory representing the incision and thus a reduction of the tube diameter of the inner tube from the original tube diameter it is particularly preferred that the trajectory representing the incision and thus a reduction of the tube diameter of the inner tube from the original tube diameter to
  • Such guidance of the trajectories results in excellent flow characteristics of the respective fluids within the fluid manifold.
  • the incisions preferably run in such a way that a wedge-shaped structure results, wherein the acute angle of the wedge can also be rounded or arcuately concave.
  • the same can preferably apply to the protuberances.
  • webs may be present in the region between the outer and inner tubes which connect the outer and inner tubes and / or webs are present in the inner tube which connect the inner wall of the inner tube and the central axis of the inner tube, ie Webs converge in the central axis.
  • this embodiment applies to the entire fluid distributor with the exception of the second aperture since, starting from the first aperture, the webs, which are present, for example, between the outer and inner tubes, have converged with the outer tube wall Footbridges used indoors are arranged at the level of the second aperture coincide with the center of the fluid distributor.
  • a core tube or a solid axis is arranged concentrically in the inner tube over the entire length of the fluid distributor, with the proviso that for this case, the second aperture in cross-section instead of the circular sectors circular sectors, wherein the trajectories of the incisions on the core tube or the solid axis terminate and in the event that webs are present in the inner tube, they connect the surface of the core tube or the solid axis with the notch base of the inner tube and the trajectories of the incisions on the core tube or the solid axis branch as soon as the notch base touches the surface of the core tube or the solid axis.
  • the core tube has openings for mass transfer.
  • the respective exchange openings can be fluidically connected to either one of the rooms A or B, but a mass transfer can take place with both rooms.
  • the mass transfer openings of the core tube can be arranged over the entire length of the fluid distributor, but also only in certain areas.
  • the fluid distributor comprises a further tube arranged longitudinally from the first aperture or the second aperture concentrically around the outer tube and enclosing a space C lying between the further tube and the outer tube, as well as a tube in the longitudinal direction after the second aperture arranged third aperture having in cross section 3n circular sectors, where n is an integer ⁇ 1, preferably ⁇ 2, and the sectors alternately with space A, space C, space B and space C and so on , wherein between the second and the third aperture the outer tube is arranged longitudinally around the circumference of the tube n incisions at the level of the boundaries of the circular sectors and alternately arranged n outcuts of the circular sectors, wherein
  • Incision has a Trajekto ⁇ e which reduces the radius of the outer tube, starting from the original radius of the outer tube at the height of the second aperture along the direction of the third aperture, wherein all Tra ⁇ ekto ⁇ en the incisions at the height of the third aperture in the center of the cross section of the fluid distributor, and each protuberance has a trajectory which steadily increases the radius of the outer tube from the original diameter of the outer tube to the height of the second aperture along the direction of the third aperture, all trajectories of the third aperture protuberances coinciding with the third aperture converge another tube
  • This embodiment of the invention is based on the same principle as the general principle of the present invention, namely that by the transition from an inner tube disposed around an outer tube by notches or protuberances of the tube therein, a course of the spaces that lie between these tubes , can be adjusted so that at the exit aperture a segment-like side by side of the formerly concentric arranged spaces can take place.
  • the erfmdungsgelaute concept which was described in the preceding paragraph, is However, not limited to the three spaces mentioned A, B and C, it can connect to the third aperture described there, which is in fluidic contact with three different rooms A, B and C, even more concentric tubes, so that the concept any number of different spaces can be expanded
  • a rotationally symmetrical heat and / or material exchanger whose cross-section has at least 2n sectors separated from one another by a membrane, where n is an integer 1, preferably ⁇ 2 with respect to the sectors which are suitable for the above-described heat and / or material exchangers likewise represent circular sectors
  • the special embodiments already mentioned for the fluid distributor also apply, for example with regard to the uniform distribution of the respective segments or the flat cross sections of the individual segments which are to be associated with the spaces A or B.
  • the membrane is material impermeable or at least partially permeable to material.
  • the membrane is impermeable to material but has good heat-conducting properties In this case, for example, metals or metal sheets
  • semipermeable membranes or porous membranes are preferred.
  • at least some of the sectors are at least partially equipped on the inside and / or outside with Sorptionsmate- ⁇ alien
  • the heat exchanger and / or material exchanger comprises a core tube arranged in the center of the heat exchanger and / or substance exchanger or a solid axis, with the proviso that annular sectors are present instead of the circular sectors, the core tube having openings for mass transfer
  • This embodiment of the heat exchanger and / or substance exchanger thus correlates with the above-described embodiment of the fluid distributor, in the event that the latter also has a core tube or a solid tube in the center
  • an apparatus for heat and / or mass exchange which comprises a heat and / or material exchanger, as described above, wherein at least at one end or both ends of the heat and / or mass transfer a previously described Fluid distributor over the second aperture is form-fitting, wherein the number of sectors of the heat and / or mass exchanger and the fluid distributor is identical
  • the two components are so merged, that the respective sectors of the fluid distributor and the heat and / or material exchanger congruent must come to rest, ie not only the number of sectors of the fluid distributor and the heat and / or mass exchanger must be identical, also the geometry of the sectors (for example, in the case that the sectors representing the space A and the sectors, the represent the room B, in the transverse must not be the same area at the height of the second aperture) must be identical.
  • the term positive fit may also include that the heat exchanger and the heat exchanger are firmly connected to one another, e.g. welded, glued, etc., are.
  • the heat and / or material exchanger and the at least one fluid distributor are axially rotatable relative to one another, wherein the rotation is preferably carried out by means of a motor.
  • the individual components can also be separated by a small gap.
  • the present invention will be explained in more detail below with reference to the attached figures, without restricting the invention to the parameters presented there.
  • the invention described herein relates, in a first aspect, to a fluid distributor I, which starts from concentric inlet and outlet tubes for the fluids A (inner tube) and B (annular space between the inner and outer tube) and can be completely accommodated in a straight tube, which corresponds in outer diameter to the outer inlet and outlet pipe.
  • heat exchange refers to the exchange of heat between the non-mixing fluids through impermeable walls
  • mass transfer refers to applications where substances are transferred through the walls (e.g., filtration processes).
  • heat and mass transfer can also be transferred via fabric particles transferred through the walls.
  • Adsorption involves attaching a substance to the sorptive coating, but not transferring it to the secondary side.
  • the adsorbed substance is expelled, for example, by thermal desorption with a hot medium following the Adsorption through the same (primary) channels.
  • Em such fluid distributor I is shown for example in Figure 1 in detail
  • the fluid distributor I is limited by an outer tube 3 and has at the height of the first aperture 1 an inner tube 2.
  • FIG. 1 shows the viewing direction of the second aperture 4, which has the various segments (in this case 6), which result from the transition from the two tubes 2 and 3, which are present on the first aperture side 1, to the segments corresponding to the spaces A (this is the space enclosed by the pipe 2) and B (this is the space lying between the pipes 2 and 3) are the same in this case, ie the individual segments are arranged at an angle of 60 ° to each other.
  • the transition between the first aperture 1 and the second aperture 4 is designed such that the inner tube 2 has both notches 5 and protuberances 6, wherein the notches of the tube 2 with increasing course from the first aperture 1 to the second aperture 4 towards Center converge and meet at the center of the aperture 4.
  • the notches 5 rejuvenate the
  • the tube 2 as well protuberances 6, which expand from the original tube diameter of the tube 2, the tube diameter and converge at the height of the aperture 4 with the outer tube 3.
  • the ratio of the cross-sectional areas of the inner tube 2 (fluid A) and the annulus between tube 2 and 3 (fluid B) can be the same fluids and similar mass flows, for example, be 1, so that both cross-sectional areas are the same.
  • the fluid distributor is constructed in such a way that the inside
  • FIG. 3 shows the Em- and the outlet cross-section (inlet aperture 1 and outlet aperture 4) of a distributor I with 6 circular sectors
  • the special feature of the distributor consists in that the cross section continuously changes from concentric circles to circular sectors, on the one hand increasing the diameter of the inner tube and, on the other hand, introducing wedge-shaped incisions 5, which are advantageously dimensioned such that they compensate the increase in area due to the growing diameter It is achieved that the cross-sectional areas for fluid A and B and thus their flow rates remain the same throughout the manifold A transition from the aperture 1 to the aperture 4 is illustrated by several cross-sectional images in Figure 4, the changes in the circumference of the inner tube 2 g It can clearly be seen that, although the diameter of the outer tube 3 remains constant over the entire length from the aperture 1 to the aperture 4, but in the tube 2 Notches 5 and protuberances 6 are mounted, wherein the notches 5
  • the specified ratio of the cross-sectional areas for the fluids A and B may also differ significantly from 1, z B if it is fluid A to water and fluid B to In this case, the narrow sectors z B are given the character of water-cooled fins (see FIG. 1 a).
  • a fluid distributor with 15 channels A and 16 channels B with an ash ratio A is shown / B >> 1 shown
  • it is advantageous to determine the increase in diameter and the course of the wedge points is a sinusoidal course
  • the incisions 5 need not be wedge-shaped, they may also be rounded, for example, which may have a positive effect on the flow (FIG. 5).
  • the main advantage of the invention is that the distributor has a dual function It distributes the fluids continuously and at the same time serves as (pre-) heat and / or material exchanger. From the beginning, heat and / or substance can be transferred Outside surface of the inner tube 2 instead, the exchange surface between the fluids is then increased continuously until the final cross-section is achieved with circular sectors, where she finally reaches her maximum. The number of sectors determines the absolute maximum of the exchange area. Due to the construction, none of the sectors is distinguished from the others and the flow is gradually diverted - without abrupt changes of direction. As a result, a uniform flow is achieved with low pressure drop, so that together with an efficient heat and / or mass transfer a high overall efficiency can be achieved with a compact, modular design.
  • the inlet and outlet cross sections 1 and 4 are circular, eliminates the otherwise often common transition pieces that increase pressure loss, cost and space requirements.
  • only the inner tube 2 must be performed before and after the distributor I through the wall of the outer tube 3 (eg via elbows), or the inlet or outlet of the annular space takes place axially or (semi-) radially in one Distance to the inlet or outlet of the inner tube.
  • Various such guides of the fluids A and B and the respective tubes 2 and 3 are shown in Fig. 6, wherein the guide is not limited to the arrow directions.
  • FIG. 7 of the construction described above has in the inner and / or in the outer part of the manifold webs (ribs) 7 and 8, which are internally connected to the central axis and the outside with the outer tube 3.
  • the inner webs 8 each lead from the wedge base radially to the central axis; the outer webs 7 lead radially from the outer contour of the distributor to the outer tube 3 and lie in each case on the bisector between two inner webs.
  • the webs increase both the stability of the construction and, in the case of a heat exchanger, the heat transfer between the fluids. because heat is transported radially by conduction through this fin construction to the exchange surface between the fluids.
  • FIG. 8 shows, in analogy to the explanations with regard to FIG.
  • a plurality of cross sections along the fluid distributor from aperture 1 to aperture 4, as a course of the geometric configuration of the inner tube 2 is designed if both between the inner tube 2 and the outer tube 3 webs 7 and in the interior of the inner tube 2 webs 8 are arranged.
  • the webs 8 in course on the aperture 4 also due to the fact that the incisions 5 converge toward the center of the fluid distributor towards the center converge and disappear, while the webs 7 between the protuberances 6 and the outer tube 3 are and even here at the aperture 4 disappear.
  • the result is an extremely stable structure of the fluid distributor, in particular because the inner tube 2 is firmly fixed by the webs 7 in the outer tube 3. This becomes particularly evident in splitters with many sectors ( Figure 9).
  • the pressure loss increases, so that the decision whether to use webs, also depends on the consideration of the total energy balance. Also constructions with webs can be made rounded (Fig. 10).
  • FIG. 11 This cascading can theoretically be continued as desired; with another fluid D, for example, the order ADCDBDCDADCDBDCD was achieved.
  • the fluid C may also be supplied to an annular space surrounding the first distributor, as indicated for example in FIG. 11 in the fifth image from the left.
  • the first manifold is enclosed by a further tube 10 and fed to a third fluid C.
  • a deformation of the first fluid distributor takes place at the height of the partitions forming the segments (notches 12) and protuberances 13 at the height of the segments towards the further tube 10, so that a segment-like alternating juxtaposition of the three fluids A, B and C at the height of the third aperture 11 results.
  • the apparatus could be used as a fuel cell, in which A (oxygen) and C (hydrogen) react to B (water) between A and C is an electrolyte membrane, between C and B is a water-permeable membrane
  • Both fluid distributor I and heat exchangers can also be equipped with a core tube K or a solid axis are constructed.
  • the core tube is to be considered in the calculation of the cross-sectional areas As soon as the wedge touches the core tube, the tip is replaced by a circular arc, so that at the outlet of the distributor no longer circular sectors, but circular sectors arise. The transition from the wedge to the circular sector must also be taken into account when calculating the cross-sectional areas
  • Figure 12 shows sections through a fluid manifold I with core tube K
  • Figure 13 is the three-dimensional impression of the transition from the wedge to the circular sector sketched
  • openings between the fluid channels and the core tube provided, which allow fluid can flow into the core tube. This may be useful, for example, if fluid A is used for cooling fluid B and accumulates in this condensate, which is to be removed via the core tube K.
  • vertical installation of the apparatus may be advantageous.
  • the channels can be drained one after the other by turning the distributor.
  • the device can be installed at any angle.
  • the core tube can also be used to supply fluids.
  • the present invention relates to a heat and / or material exchanger II, which is shown in FIG. 2 a as a separate component, which is provided with two fluid distributors 1 a and 1 b, which are each at the ends of the heat and / or mass exchanger II can be arranged, is shown.
  • the respective circular sectors which can be connected to the fluid distributors Ia and / or Ib, are arranged identically to the resulting divisions of the circular segments on the aperture 4 of the fluid distributor Ia or Ib.
  • the segments of the heat and / or mass exchanger II run parallel to one another.
  • the membranes may be permeable to fabric and / or fabric impermeable.
  • a core tube may be arranged in the heat and / or material exchanger II.
  • the present invention relates to a heat and / or material exchange apparatus III, which is shown for example in FIG. 2b, and from the assembled parts, which are shown in Figure 2a, is arranged.
  • the apparatus consists of two fluid distributors Ia and Ib flanking a heat and / or material exchanger II at its respective ends.
  • the apparatus III consists of at least one, usually two symmetrically arranged fluid distributors Ia and Ib and usually, but not necessarily, from an intermediate heat and / or material exchanger II ( Figure 2b). It can be operated both in DC and in countercurrent.
  • the construction of the apparatus makes it possible to divert the fluid flows into different channels by rotating at least one distributor Ia and / or Ib and / or the heat or material exchanger II around the angle of a circular sector. For example, it is possible to allow fluid A in the inner tube and fluid B to enter the annular space and, depending on the rotation, either fluid A in the inner tube and fluid B in the annular space or fluid A in the annular space and fluid B in the inner tube. In this way, different channel connections can be switched using stepper motors, so that valves can be omitted.
  • the distributor receives a third function; he is thus fluid distributor, heat and / or material exchanger and actuator in a component. This function can be used especially if the channels have different functions and the fluids alternately have these functions should use.
  • a sorption heat exchanger which can be used for example for solar air conditioning.
  • a conventional plate-type sorption heat exchanger is described in EP 1 508 015 B1. This has heat exchanger and sorption channels which are in thermal contact (eg alternately stacked). On the inner surfaces of the sorption channels, a sorption material is applied.
  • the heat exchange channels contain a cooling fluid, the sorption channels a fluid from which at least one component is to be extracted, which can be absorbed by the sorption material.
  • the sorption heat exchanger also contains humidifying components for humidification or supersaturation of the cooling fluid.
  • both fluids are air of different temperature and humidity; the medium to be extracted is water, and various sorbents (for example silica gel) can be used as the sorption material.
  • the sorption heat exchanger of the prior art requires a plurality of valves to distribute different air flows to heat exchange or sorption channels. In the apparatus III described here, this can be done by rotation of the distributor Ia and / or Ib.
  • a possible mode of operation is shown below as an example for a ventilation mode (supply air is conditioned ambient air) in DC configuration:
  • the fluids at the inlet are exhaust air (inside) and ambient air (outside), the middle piece here consists of heat exchanger and sorption sectors, at the outlet are the fluids exhaust air (inside) and supply air (outside).
  • the ambient air can already be heated in a component upstream of the distributor or, for example, via the jacket surface of the outer tube at the inlet.
  • the heat exchanger ducts must be able to be humidified, so humidifiers, eg nozzles, should be provided which supply water radially to every other sector.
  • the heat exchanger and the sorption channels can be provided with further internal ribs (radially or parallel to the cylindrical surface) to increase the surface area within each sector.
  • a second apparatus A2 which carries out the same steps 1) to 7) with a time delay: while one of the apparatuses performs step 1), the other executes steps 3) to 5).
  • the fluids must be recirculated accordingly.
  • This can be done in a third apparatus A3 consisting of only two by one sector arranged distributed distributors without middle piece and in the reverse direction compared to the apparatuses Al and A2 flows through.
  • A3 / distributor 2 (inside) must be connected to Al / distributor 1 and A2 / distributor 1 via a changeover valve so that the exhaust air is blown into either Al or A2 depending on the process step.
  • distributor channels which correspond, for example, to those for fluid A in FIG. 9, can be manufactured, for example, by internal high-pressure forming (hydroforming, eg hydroforming).
  • IHU is state of the art and is widely used for the production of complex components. It is conceivable to manufacture the channels from a tube (FIG. 15) or from a partially plated sheet metal composite which is shaped by generating an internal pressure in the regions not connected by a previously applied separating means (FIG. 16). In both cases, the shaping is achieved by forming in a suitable tool (pressing into the tool by internal pressure). Another possibility is to weave the channels three-dimensionally (this technology already exists) and then optionally stabilize them with a hardening material, such as epoxy resin.
  • a hardening material such as epoxy resin.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Dispersion Chemistry (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)

Abstract

L'invention concerne un répartiteur de fluide, un échangeur de chaleur et/ou de matière, ainsi qu'un appareil présentant au moins un répartiteur de fluide ainsi qu'un échangeur de chaleur et/ou de matière placé sur ce dernier.
EP09795934.0A 2008-12-19 2009-12-21 Distributeur de fluides a symetrie de rotation Not-in-force EP2379978B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL09795934T PL2379978T3 (pl) 2008-12-19 2009-12-21 Dystrybutor płynów z symetrią obrotową

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008063866 2008-12-19
PCT/EP2009/009184 WO2010069602A2 (fr) 2008-12-19 2009-12-21 Appareil pour la répartition de fluides et leur échange de chaleur et/ou de matière

Publications (2)

Publication Number Publication Date
EP2379978A2 true EP2379978A2 (fr) 2011-10-26
EP2379978B1 EP2379978B1 (fr) 2014-02-12

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP09795934.0A Not-in-force EP2379978B1 (fr) 2008-12-19 2009-12-21 Distributeur de fluides a symetrie de rotation

Country Status (3)

Country Link
EP (1) EP2379978B1 (fr)
PL (1) PL2379978T3 (fr)
WO (1) WO2010069602A2 (fr)

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GB2474529B (en) * 2010-03-10 2011-09-21 Green Structures Ltd Ventilation system
DE102012022363A1 (de) 2012-11-15 2014-05-15 GM Global Technology Operations LLC (n. d. Gesetzen des Staates Delaware) Interner Wärmetauscher für eine Kraftfahrzeug-Klimaanlage
DE102013207180A1 (de) * 2013-04-19 2014-10-23 Behr Gmbh & Co. Kg Wärmeübertrager mit in einem Sammelkanal angeordneten Einsatz
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EP2379978B1 (fr) 2014-02-12
WO2010069602A3 (fr) 2011-01-13
WO2010069602A2 (fr) 2010-06-24
PL2379978T3 (pl) 2014-07-31

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