EP0283718B1 - Echangeur à contre-courant - Google Patents

Echangeur à contre-courant Download PDF

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Publication number
EP0283718B1
EP0283718B1 EP88102398A EP88102398A EP0283718B1 EP 0283718 B1 EP0283718 B1 EP 0283718B1 EP 88102398 A EP88102398 A EP 88102398A EP 88102398 A EP88102398 A EP 88102398A EP 0283718 B1 EP0283718 B1 EP 0283718B1
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EP
European Patent Office
Prior art keywords
ducts
heat exchanger
counter
duct
air
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.)
Expired - Lifetime
Application number
EP88102398A
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German (de)
English (en)
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EP0283718A1 (fr
Inventor
Johann Schönhammer
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Individual
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Individual
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Publication date
Priority claimed from DE8704409U external-priority patent/DE8704409U1/de
Priority claimed from DE8712948U external-priority patent/DE8712948U1/de
Application filed by Individual filed Critical Individual
Priority to AT88102398T priority Critical patent/ATE56534T1/de
Publication of EP0283718A1 publication Critical patent/EP0283718A1/fr
Application granted granted Critical
Publication of EP0283718B1 publication Critical patent/EP0283718B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F7/00—Elements not covered by group F28F1/00, F28F3/00 or F28F5/00
    • F28F7/02—Blocks traversed by passages for 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
    • 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
    • F28D9/0031—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 for one heat-exchange medium being formed by paired plates touching each other
    • 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
    • F28F1/025—Tubular elements of cross-section which is non-circular 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
    • F28F3/02—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations
    • F28F3/04—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element
    • F28F3/042—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element
    • F28F3/046—Elements or assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with recesses, with corrugations the means being integral with the element in the form of local deformations of the element the deformations being linear, e.g. corrugations

Definitions

  • the invention relates to a counterflow heat exchanger according to the preamble of claim 1.
  • Such a heat exchanger is known from DE-A 3 102 523.
  • Such heat exchangers are work tools that are used in particular in agriculture for stable ventilation and ventilation, but also for commercial spaces. Some applications require a non-flammable or flame-retardant version.
  • the heat exchangers are used to warm up the cold supply air in winter by means of the warm exhaust air and thus to improve energy efficiency and enable higher air exchange rates.
  • To operate the supply and exhaust air system with a heat exchanger only two blowers are required.
  • Fanthermore at least the heat exchanger block installed vertically in a shaft or chimney is free of operating costs and maintenance; in particular, it cleans itself through the condensation water that collects on the walls and runs downwards .
  • the heat exchangers are therefore preferably installed with vertical channels, but at least with a significant vertical component. With such heat exchangers, efficiencies above 50% have already been achieved.
  • the known countercurrent heat exchanger according to DE-A 3 102 523 is designed as a film honeycomb heat exchanger with vertical channels and the throughflow channels are formed according to one embodiment from wave paths made of plastic, which are composed such that they form the parallel vertical air channels.
  • the cross-sectional areas of the ascending exhaust air ducts alternate with the cross-sectional areas of the descending supply air ducts in horizontal sectional planes in the main directions.
  • the channels are also formed by hollow profile plates, the hollow chambers of which have an elliptical profile.
  • the invention has for its object to further improve the efficiency of the counterflow heat exchanger without accepting other functional disadvantages by increasing the temperature differences prevailing through the respective walls.
  • the invention characterized in claim 1 or 6. It relates to non-rotationally symmetrical first channels, i.e. with a non-circular cross section that coils along the channel length, or first or second channels with a changing cross-sectional area along the channel length, with the changing characteristics resulting in good air swirling or air displacement and an outward direction - and flow between adjacent first or adjacent second channels takes place, so that medium is always brought from the inside with the original temperature to the partition between the channels. According to an optimal concept, these two aspects are combined.
  • the marked invention on the one hand with the alternating spiraling of the channel cross-section along the extension of the first channels, i.e. in particular with helically turning back and forth edges or cross-sectional axes with a sudden change, whereby, for example, two but also more sections of alternating spiral directions may be present 1 to 5 -, and on the other hand with the changing cross-sectional area and the resulting displacement of the medium - claim 6 - results in such a coiled or pulsating design that in these first or second channels and also in the oppositely flowing second or first channels, the intervening, swirling the air streams and detaching them again and again from the partition, so that a warm core column does not rise within these channels, which are, for example, the ascending exhaust air ducts, largely without contact with the heat exchanger wall up to the upper air vent more, the air in the channels is put into a sharply reversed swirl or back and forth movement between the channels, as a result of which there are constantly changing portions in the heat-exchanging wall contact
  • the turbulence of the air flows can be increased by additional measures, in the supply air ducts also by air baffles - which would interfere with the self-cleaning effect in the exhaust air ducts.
  • Claim 4 specifies additional measures in this regard, in particular a progressive swirl between the change points being considered expedient.
  • a special embodiment according to claim 5 provides that the rotation of the cross sections of the first channels is accompanied at the same time by an offset of the cross sectional center points, in particular in such a way that in the projection of the channel onto the horizontal there is no surface which is completely only from top to bottom assigned channel. This also avoids that a medium thread of air remains along the longitudinal axis of the channel, which contributes little to the heat exchange.
  • the first channels in particular the warm exhaust air channels
  • the first channels flow through in the same direction, only touch one another point by point, possibly via short webs.
  • special swirl chambers can be inserted along the channels, in particular at the helix or surface change inflection points, which can in particular have the configuration of hollow cubes.
  • the air flow which flows in with a twist in particular, gets caught on the inner surfaces of the cubes and thereby mixes again. If the active chambers are roughly round, they serve as relative quiet distances in the length of the heat exchanger. By choosing the length of these swirl chambers, an adjustment can be made between the length of the heat exchanger and the fan power available.
  • the channels can be formed in a manner known per se (DE-AS 1 102 191, DE-PS 3 102 523) from profile plates which, however, have a profile not only in horizontal section but also in vertical section. With a suitable design, profile plates of a single profile are sufficient, which are joined together, which considerably simplifies storage and assembly.
  • connection of the profile plates is advantageously carried out according to claim 12, wherein the air has to alternate between the channels, which leads to increased turbulence.
  • the measure according to claim 13 further promotes the air exchange between the channels.
  • a vertical, ie vertical, arrangement is preferred due to the desired self-cleaning effect, in particular of the exhaust air ducts.
  • a horizontal arrangement according to claim 14 which is easier to install in some existing buildings.
  • the closed first ducts would then have to be the fresh air ducts and their interspaces, which are open to one another, i.e. the second ducts should be the exhaust air ducts and contain a sprinkler system, with the aid of which the dirt deposits from these second ducts, i.e. from the outside of the closed ducts, were washed out can be.
  • Fig. 1 illustrates a section, namely a length range, of a heat exchanger in a stretched design, as it should most likely come close to practical implementation. It is a sectional illustration in one plane: corresponding to I-I in FIG. 2, which shows the heat exchanger a little more crowded 3 for better illustration. FIG. 3, finally, shows cross sections in height planes a, b and c, while further cross sections in FIG. 2 are indicated by axis crosses at the same heights.
  • the heat exchanger has closed first channels through which flow flows in parallel in a first direction, between which second channels communicating with one another and through which flows in parallel in the opposite sense.
  • the first ducts are exhaust air ducts 1 and the second ducts are supply air ducts
  • FIG. 3 thus shows a section of a total of one in three horizontal sections a, b and c (FIG. 1) that are relatively close in height Block-forming duct system of a countercurrent heat exchanger, with the exhaust air ducts 1, whose elliptical cross section is coiled by its long elliptical axis 2 rotating from the bottom upwards, so that the ends of the axes 2 each describe helical lines 2 '. It is assumed that section a is in one plane in the lower area of the heat exchanger block.
  • the axis 2 of the exhaust air duct 1 located at the top right in the illustration lies in the sectional plane a parallel to the front and rear edge of the picture.
  • the axis 2 of this channel already has an angle of approximately 20 ° to the front and rear picture edge and in the section plane c of 40 ° . 1 and 2, the rotation continues like a screw from bottom to top until a point of sudden change, with rotations of more than 360 ° being achieved, depending on the height of the heat exchanger block and its continuous length sections.
  • the exhaust air ducts 1 and the supply air ducts 3 are separated from one another by relatively thin, essentially upstanding walls 4, between which a heat transfer from the exhaust air ducts 1 to the supply air ducts 3 takes place. Due to the abruptly changing swirl that the coiled exhaust air ducts exert on the respective air flow flowing therein, the air is constantly swirled again and comes loose from the wall to be replaced by air from the center, so that the entire area is evenly involved Air volume is taken care of at the heat exchange process. The helical rotation of the cross-sectional dimension of the exhaust air ducts 1 also increases the surface of these ducts and thus the heat exchange surface. In the embodiment according to FIGS.
  • the supply air is also swirled considerably, namely by changes in its cross-section, which force an air displacement between the individual supply air ducts 3, as indicated by arrows in FIG. 3.
  • sections 3b on the one hand and 3c on the other hand somewhat different designs and symbols are symbolized with regard to air displacement, as will be described below.
  • the condensed water that settles on the wall inside the exhaust ducts. 1 runs freely ? , down the wall and cleans the inner wall of the exhaust air ducts in a manner known per se, which is promoted by the corner-free construction of these ducts.
  • the condensed water is caught and drained at the bottom. Less dirt and hardly any condensation water collects in the supply air ducts 3, so that local acute-angled corner edges of these ducts do not impair.
  • Correspondingly twisted duct lines with an elliptical cross section can be used to construct the heat exchanger according to FIGS. 1 to 3.
  • the respective sectional view of the individual profile plate 5 is shown separately for the outermost of the wall regions shown in the sectional views of FIG. 3.
  • the two profile plates 5, each forming a channel row are expediently connected, in particular glued, to coupling strips 7 'which lie between the channels. They can also be fixed locally to one another by small profiles or plug-in means, so that the generally not very rigid plate stacks receive and maintain correct alignment.
  • FIG. 4 shows the arrangement of elliptical channels in a slightly different pattern. While the two orientations alternated in each section plane according to FIG. 3, according to FIG. 4, adjacent channels have axes 2 parallel in one basic direction and axes 2 perpendicular to one another in the other basic direction.
  • FIG. 4 shows such an embodiment constructed from profile plates 5. The plates 5 are again, as described with reference to FIG. 3, glued together on the coupling strip 7 'to form the channel rows and tacked together from channel row to channel row at coupling points 7 which are spaced apart in the vertical direction.
  • the channels are arranged in rows 8 and columns 9, and in the illustrated embodiment the longer axes 2 of the channels 1 of each column are parallel to each other in each horizontal section plane.
  • the profile plates 5 therefore have the same profile in all sectional planes for all rows and their opposite sides, but for the opposite sides in an upside-down arrangement.
  • the heat exchanger block can therefore be assembled from the same profile plates.
  • FIGS. 5 and 6 show arrangements corresponding to FIGS. 3 and 4, but with a modified channel cross-sectional shape, which is diamond-shaped according to FIG. 5 and trapezoidal according to FIG. 6. As shown in FIG. 5, edges 2 'and 3', which in the diamonds of FIG. 5 are located at the ends of the diamond axes 2 and 3, describe helical lines along the channel.
  • FIG. 7 shows, based on six adjacent horizontal sections a, b, c, d, e and f lying between two spiral reversal points, an embodiment which is shown using rectangular channel cross sections.
  • the cross sections could also have a different elongated shape.
  • the embodiment is characterized in that, for example, between the cuts in the sectional planes a and e or b and f the associated channels have no coverage, so that it is completely excluded that a flow column is established in a central channel core, which without exchange straight through the surrounding layers.
  • a swirl chamber 8 in the form of a hollow cuboid is used in a given rotation phase, on the two connection sides of which the direction of rotation of the channel cross sections is opposite, as shown by the lines 2 'and 3' of the axis ends.
  • the couplings 7 are arranged at intervals along the length of the channels, in each case appropriately on the swirl chambers 8, and in this way create a solid block of the heat exchanger. According to FIG. 2, these couplings 7 consist of tube pieces with centering pieces molded onto the profile plates, which are glued together.
  • the mutual distance between the channels can be selected, which has an influence on the flow resistance between the individual channels 4, between which the air flows back and forth due to the volume changes when the cross-section of the channels 1 rotates adaptation to the blower line allowed.
  • the vortex chambers 8 in the embodiment shown create in a manner known per se (GB-PS 828 992) a cross-sectional expansion of the exhaust air ducts 1 and a cross-sectional narrowing of the supply air ducts 4 formed by the intermediate space, but which is not assigned a complementary supply air duct expansion, so that it is is a pure constriction.
  • Such constrictions have an influence on the flow resistance of the heat exchanger.
  • FIGS. 8 to 10 show another embodiment which only uses air displacement for the swirling of the air streams. While the upflow exhaust ducts 1- -th their cross-sectional area substantially beibehal-, however, change the cross-sectional shape and are connected together at intervals by gaping profile plates 5, to change the supply air ducts 3 to their throughflow considerable ist i, whereby the generally downwardly ströde supply air to a constant change between adjacent channels is forced. As a result, fresh, cool supply air is always brought back to the duct walls, in which heat is released on the inside, in particular by condensation of condensed water in the exhaust air. In the areas 13, in which the profile plates 5 on the strips between the exhaust air ducts 1 are not connected to one another, but gape apart, additional heat transfer surface is obtained
  • FIGS. 8 to 10 represent the cross-sectional variations on the basis of changing trapezoidal cross-sections of the exhaust air ducts 1. This is an example, obviously other crosses are also cuts, especially rounded asymmetrical cross-sections, suitable for achieving the effect.
  • FIG. 11 shows a section corresponding to a somewhat curved plane XI-XI in Fig. 1 through the coupling strip 7 '. 1 can also apply to this embodiment.
  • the profile plates 5 are only glued to one another in the area of the coupling strips 7 ′ at intervals, namely in areas 12, while they gap apart in the intermediate areas 13 and enable communication between the adjacent exhaust air ducts. This not only achieves a certain air circulation between the exhaust air ducts and thus increased turbulence, but also ensures that the supply air has to switch back and forth between the ducts to an even greater extent; this is because the "bottom" of the coupling strip 7 ', which is saddle-like flattening of the channel formed between the exhaust air channels and forming the supply air channel 3, is always present when this channel is also from the sides, that is to say from the sides Walls of the exhaust duct 1 ago, is restricted.
  • Fig. 12 shows a perspective section of a heat exchanger block in a lying arrangement.
  • the heat exchanger plates are in turn each assembled from two profile plates and the individual channels have pulsating cross sections and communication links between them, which conduct the displacement air between adjacent channels.
  • the individual profile plates 5 are made of aluminum, which can only be deep-drawn to a lesser extent and which therefore results in a relatively flat profile.
  • the heat exchanger is incombustible due to this material.
  • the relatively flat profile is particularly suitable for a lying arrangement, since the rounded edges and the moderate convexity favor cleaning by water trickling over the plates in the area of the exhaust air ducts.
  • the supply air flows are symbolized by arrows. It is evident that part of the supply air changes back and forth between adjacent ducts in the course of the narrowing and widening of the individual duct cross sections. Likewise, the exhaust air changes back and forth along the surface of the profile plates 5 between the adjacent ducts, since it too has to evade according to the different cross-sectional requirements of the supply air ducts.
  • the air displacement principle is also used in a foil waste heat exchanger, as is known from DE-PS 3 102 523, in that adjacent honeycomb passages flow through in the same direction and have connections to the honeycomb walls from one side to the other project or are immersed.

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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)

Claims (14)

1. Echangeur de chaleur à contre-courant dans un système d'amenée et d'évacuation d'air, en particulier pour la ventilation d'étables ou d'écuries, comprenant des conduits d'évacuation d'air et des conduits d'amenée d'air s'étendant parallèlement dans l'ensemble, les conduits d'évacuation d'air ou d'amenée d'air étant constitués minces qui présentent des sections transversales non circulaires, et les espaces vides entre les premiers conduits (1) formant dans chaque cas les seconds conduits (3), caractérisé en ce que les premiers conduits (1) sont vrillés et le vrillage est réalisé par segments successifs avec des sens de rotation respectivement opposés.
2. Echangeur de chaleur à contre-courant selon la revendication 1, caractérisé en ce que les sections transversales des conduits présentent chaque fois au moins un angle qui forme une arête le long du conduit, et en ce que cette arête est rendue hélicoïdale le long de l'étendue du conduit.
3. Echangeur de chaleur à contre-courant selon la revendication 1 ou 2, caractérisé en ce que les sections transversales des conduits vrillés présentent chacune un grand axe et un petit axe et en ce que, le long de l'étendue du conduit, ces axes sont tournés en sens opposés le long de segments longitudinaux alternants.
4. Echangeur de chaleur à contre-courant selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la pente des hélices varie le long de l'étendue longitudinale du conduit.
5. Echangeur de chaleur à contre-courant selon l'une quelconque des revendications 1 à 4, caractérisé en ce qu'au moins les premiers conduits (1) ne présentent pas de colonne rectiligne s'étendant d'une extrémité du conduit à l'autre extrémité du conduit (fig. 7).
6. Echangeur de chaleur à contre-courant dans un système d'amenée et d'évacuation d'air, en particulier pour la ventilation d'étables ou d'écuries, comprenant des conduits d'évacuation d'air et des conduits d'amenée d'air s'étendant parallèlement dans l'ensemble, les conduits d'évacuation d'air ou d'amenée d'air étant constitués par des premiers conduits (1) à parois de séparation minces qui présentent des sections transversales non circulaires, et les espaces vides entre les premiers conduits (1) formant dans chaque cas les seconds conduits (3), caractérisé en ce que les seconds conduits (3) voisins communiquent entre eux, au moins à intervalles, et en ce que la surface de la section transversale des seconds conduits varie le long de l'étendue du conduit, et cela en sens contraire pour les conduits respectivement voisins dans des régions individuelles de l'étendue des conduits.
7. Echangeur de chaleur à contre-courant selon la revendication 6, caractérisé en ce que la variation de la surface de la section transversale des seconds conduits (3) résulte d'un vrillage des premiers conduits (1 ).
8. Echangeur de chaleur à contre-courant selon l'une quelconque des revendications 1 à 7, caractérisé en ce que les cloisons de séparation sont unies ensemble à intervalles (en 7) pour la formation d'un bloc échangeur de chaleur.
9. Echangeur de chaleur à contre-courant selon la revendication 8, caractérisé en ce que les conduits vrillés (1) sont unis ensemble au moyen de couplages (7) qui fixent une distance réglable entre les parois des conduits qui se font face en rapport avec chaque couplage.
10. Echangeur de chaleur à contre-courant selon l'une quelconque des revendications 1 à 9, caractérisé en ce qu'il est inséré, le long des premiers conduits (1), des zones longitudinales (8) ayant une forme, en section transversale du conduit, qui change brusquement en comparaison des zones contiguës.
11. Echangeur de chaleur à contre-courant selon l'une quelconque des revendications 1 à 10, caractérisé en ce que les parois de séparation (4) sont formées par des plaques profilées (5) qui s'étendent d'une part en direction longitudinale et d'autre part en direction transversale de l'échangeur de chaleur et qui présentent un profil variable dans ces deux directions.
12. Echangeur de chaleur à contre-courant selon la revendication 11 rattachée aux revendications 6, 8 et 10, caractérisé en ce que les plaques profilées (5) sont unies entre elles par paires dans des zones de surface (7') ou entre les conduits dont les sections transversales varient en ce qui concerne la surface, et en ce qu'en direction de la l'épaisseur de l'échangeur de chaleur, ces paires de plaques profilées sont unies (en 7) aux paires de plaques profilées respectivement voisines au niveau des zones longitudinales ayant une forme, en section transversale du conduit, qui varie brusquement, tandis qu'une fente subsiste entre ces points d'union (7).
13. Echangeur de chaleur à contre-courant selon la revendication 12, caractérisé en ce que les plaques profilées (6) ne sont unies entre elle que par endroits (en 12) dans les zones de surface (7') entre les premiers conduits (1) et laissent entre elles un espace béant (en 13) entre ces points d'union.
14. Echangeur de chaleur à contre-courant selon l'une quelconque des revendications 1 à 13, caractérisé en ce que les conduits s'étendent en direction sensiblement horizontale et en ce qu'une installation d'arrosage est prévue dans la région des espaces creux entre les premiers conduits (1).
EP88102398A 1987-03-25 1988-02-19 Echangeur à contre-courant Expired - Lifetime EP0283718B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88102398T ATE56534T1 (de) 1987-03-25 1988-02-19 Gegenstromwaermetauscher.

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE8704409U DE8704409U1 (de) 1987-03-25 1987-03-25 Gegenstromwärmetauscher
DE8704409U 1987-03-25
DE8712948U DE8712948U1 (de) 1987-09-25 1987-09-25 Gegenstromwärmetauscher
DE8712948U 1987-09-25

Publications (2)

Publication Number Publication Date
EP0283718A1 EP0283718A1 (fr) 1988-09-28
EP0283718B1 true EP0283718B1 (fr) 1990-09-12

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EP (1) EP0283718B1 (fr)
DE (1) DE3860582D1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
EP1815902A1 (fr) 2006-01-19 2007-08-08 Martin Schönhammer Epurateur d'air vicié doté d'un échangeur thermique pour une écurie

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EP0359358B2 (fr) * 1988-09-14 2001-10-24 Showa Aluminum Kabushiki Kaisha Condenseur
FR2865028B1 (fr) * 2004-01-12 2006-12-29 Ziepack Echangeur thermique et module d'echange s'y rapportant
FR3020135A1 (fr) * 2014-04-16 2015-10-23 Commissariat Energie Atomique Module d'echangeur de chaleur a echange thermique et compacite ameliores, utilisation avec du metal liquide et du gaz.
CN109489449A (zh) * 2018-11-20 2019-03-19 英特换热设备(浙江)有限公司 一种暖气片
CN115077267B (zh) * 2022-08-19 2023-01-20 中国核动力研究设计院 换热构件和冷凝器

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DE3102523C2 (de) * 1981-01-27 1985-10-10 Ludwig 8448 Leiblfing Penzkofer Gegenstromwärmetauscher

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1815902A1 (fr) 2006-01-19 2007-08-08 Martin Schönhammer Epurateur d'air vicié doté d'un échangeur thermique pour une écurie

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EP0283718A1 (fr) 1988-09-28
DE3860582D1 (de) 1990-10-18

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