HUE034718T2 - Heat exchanger - Google Patents

Description

(12) Date of publication and mention (51) Int Cl .: of the grant of the patent: F28D 7110 <2006 01> F28F 1106 <200e 01> 19.07.2017 Bulletin 2017/29 F28F 1IO8 < 200601> B21D 53106 <2006 01> (21) Application number: 10726891.4 (86) International application number: PCT / EP2010 / 002656 (22) Date of filing: 30.04.2010 (87) International publication number: WO 2010/124871 (04.11 .2010 Gazette 2010/44)

(54) HEAT EXCHANGER wArmetauscher

ECHANGEUR DE CHALEUR (84) Designated Contracting States: · ZAKRZEWSKI, Thomas, Zenon AT BE BG CH CY CZ DE DK EE ES MS IT MS EN NL EN PL · WALTER, Leonid PT RO SE SI SK SK TR 76532 Baden-Baden (DE) (30) Priority: 30.04.2009 EP 09159260 (74) Representative: Eaton IP Group

29.05.2009 GB 0909221 EMEA

Eaton Industries Manufacturing GmbH (43) Date of publication of application: Route de la Longeraie 7 07.03.2012 Bulletin 2012/10 1110 Girls (CH) (73) Proprietor: Eaton Industrial IP GmbH &amp; Co. KG (56) References: 12529 Schonefeld (DE) EP-A1- 1 840 495 EP-A1-1 895 256 JP-A-2002 318 015 JP-A-2004 278 854 (72) Inventors: JP-A - 2006 162 241 US-A-4 194 560 • HILGERT, Andreas, Richard US-A1- 2006 096 314 76547 Sinzheim (DE) • KLUG, Peter, Tobias 77933 Lahr (DE)

description

TECHNICAL FIELD

[0001] The invention relates to the use of air conditioning systems for automotive applications.

BACKGROUND

[0002] Air-conditioning systems of motor vehicles, for example, are a so-called internal heat exchanger. This is an air-conditioning system that can be used as a heat transfer device. . One example of an inner heat exchanger is disclosed in DE10 2006 017 816 B4. This document discloses a single piece extruded aluminum heat exchanger element. In this one extruded profile channels are formed for both liquid and suction side refrigerant. Whilst the extruded heat exchanger elements of the exchange rates are the most common, they are suffering from certain drawbacks; welding or brazing must be used in order to connect to the profile; the extrusion tool is also an extrusion tool.

[0003] In order to achieve the desired heat transfer, the heat exchanger must have a given heat exchange area. Sometimes, space is at a premium, for example in automotive applications. In such cases it is possible to use heat exchangers. U-shaped pipe or into other shapes so that it can be installed in a given space. This in-turn requires that the heat exchanger pipe be designed in a manner that is suffi- ciently free of collapsing its fluid conveyance channels. Moreover, it may also mean that the heat exchanger is limited or constrained.

[0004] In this regard, it is necessary to provide a heat exchanger for the above mentioned problems.

[0005] Heat exchanger and method in the preamble of claims 1 and 9 are known from US 4,194,560. Dent portions are alternately formed by the outside face of the inner tube. The inner tube is then fitted inside the outer tube to the inside tube and inner tube with oil flows in the zigzag fashion to as sure heat transfer. Due to the dents formed in the inner tube, the cross-sectional area of the inner tube is reduced in relation to the original rooms. Inside the inner tube. In addition, it is also known as the drop of the outer and inner tube.

SUMMARY

[0006] According to the present invention there is provided a heat exchanger and a method of manufacturing claims.

BRIEF DESCRIPTION OF THE DRAWINGS

[0007] \ t [0007] \ t

Fig. 1 is a schematic diagram of an internal heat exchanger;

Fig. 2 shows a schematic illustration of the internal heat exchanger shown in Fig. 1 in a U-shaped configuration;

Fig. 3a shows a perspective of the future;

Fig. 3b shows the exterior of the exterior exterior of the exterior;

Fig. 3c shows the exterior of the inner tube of the inner tube;

Fig. 3d shows a schematic illustration of the inner tube of the inner tube of the inner tube;

Fig. 4 is an image schematically illustrating part of the inner tube, which illustrates one exemplary method of creating a portion of the inner tube;

Fig. 5a to FIG. 5c show cross sectional views of the internal heat exchanger;

Fig. 6 is a schematic illustration of the internal heat exchanger of the first;

Fig. 7 shows part of an image of Fig. 4, showing the performance of the inner tube

internal heat exchanger of the firstaut; DETAILED DESCRIPTION

Referring now to the drawings, several embodiments of the present invention are shown in detail. The drawings are not to the point and can be exaggerated. Further, the embodiments set forth here are not intended to be exhaustive or otherwise restricted to the following detailed description.

Referring to FIG. 1 air conditioning system 1 suitable for use in a motor vehicle is schematically illustrated. The air conditioning system 1 includes a compressor 2, which may be driven, for example. The compressor 2 has an inlet 4, connected to a low pressure line, at low pressure. The compressor 2 also has an outlet 3, via pressurized refrigerant is output, in a high pressure line. Therefore, the cooling device 6 is also referred to as a condenser. In this example, the refrigerant used is R-134a that works at low pressure.

11. The internal heat exchanger 11 has a high-pressure outlet 12. 14. The expansion valve 15 is the evaporator 16 and, as a result, absorbs thermal energy from the high pressure line. environment; in this example, cooling the airsupplied to the interior of the motor vehicle. The resultant refrigerant vapor is then transported from the evaporator 16, via the internal heat exchanger 11 in a counter-current direction. 9. In so doing, the refrigerant vapor cools the pressurized refrigerant, thus itself becoming heated. 11. It is then conducted, via the low-pressure line 21, to the inlet 4 of the compressor 2.

[0011] The internal heat exchanger 11 allows for an increase in the temperature of the compressor. Therefore the cooling device 6 At the same time, the internal heat exchanger 11 lowers the temperature of the evaporator 16 and ambient air. In this continent, the internal heat exchanger 11 may be used.

[0012] FIG. In this example, it will be appreciated that it will be appreciated. However, in certain applications, but not all, bending of the heat exchanger 11 is required. Where it is required, the coaxial tube should be able to be at least without the flow flow or collapse or break. The bent pipe 22 has two legs 23, 24, that are bent away from each other at their upper ends.

[0013] The high-pressure inlet of the system 1 at position 26a. The low-pressure inlet of the system 1 at position 26b. 26a and 26b are located at or close to the end of the pipe.

Referring now to Figs. 3a-3d, the structure of the internal heat exchanger 11 will be described in more detail. Fig. 3a shows a view of the internal heat exchanger 11 ofafirst in its assembled state but prior to being bent into its final U-shaped configuration. 30 years old, inside the tube 30 and the inner tube 32 being designed as refrigerant conduits . The inner tube 32 is located inside and out of the outer tube. 30 are 18mm and 20mm, respectively. 30 and can be seen in the figure are 12mm and 15mm, respectively. 30 and inner tube 32 are selected for the application. The inner diameter of the outer tube 30 may from range 9-19m for automotive or car applications, 20-39mm for bus applications and, 23-50mm for train applications. In one example having the refrigerant, the outer tube is 24mm outer diameter with a 20mm inner diameter. The starting material, or base tube, is an 18mm outer diameter with an inner diameter of 15mm.

11. Each of these is a suitable orifice in the outer tube 30 using a conventional process such as welding or brazing. The weld points are referenced 34 in the figure. A fluid connection is formed between the high-pressure inlet and the outer tube 30. In this continent, the outer tube 30 may be used as a connection. The Extreme End Points 36 of the Outer Tube 30 are joined to the inner tube. Again a conventional process may be used; for example o-rings, crimping and or brazing. Fig. 3b shows a photograph of an internal heat exchanger. 3a [0016] 32a and 32b that are circular. These are the types of material that can be found in the body. In this example, the end portions 32a and 32b are unmodified base tube material. Therefore, the end portions 32a and 32b may be configured to be the required lengths for the function of low pressure tubes 21 and 17, shown in FIG. 1. This is a means of turning connection tubes that were needed; thus obviating the need for costly connection processes, such as welding and eliminating risk.

Between the end portions 32a and 32b of the inner tube 32c that has been deformed into a helical shape along its longitudinal axis. The inner tube of the internal heat exchanger is shown in FIG. 3c. The central portion 32c may be deformed using any convenient deforming procedure. This is a deformed through aart clamping process. However, other deforming processes or apparatus such as press or hammer may be used. In this example, the clamping process is using the opposing clamping surfaces to achieve the desired exterior profile of the portion 38b. The marks are shown in Fig. 38a. 3c. Furthermore, it can be seen from Fig. 3c that deformed portion 32c has a helical profile. Illustrated in Fig. 32c illustrated in Fig. 3d.

Referring to FIG. 4 the method of manufacturing elliptical helix of central portion 32c, will now be described. Fig. 4 shows an image schematically illustrating a part of the inner tube 32 is not deformed 32 is circular is cross section. Adjacent to the left hand end 32a end of the inner tube 32 is portion 44a that has been deformed to an approximate elliptical shape of predetermined dimensions. These dimensions may be controlled by the parameters of the deforming process; examples of the clamping surfaces of the clamping surfaces.

The figure of the elliptical portion 44a is shown orientated vertically. 32 is the best time to get the rest of the tube. fixed angle in a given direction about its longitudinal axis; in this example 45 degrees. The clamping operation is thenalt. 32b of the inner tube 32, as is illustrated by deformed portions 44b - 44f. This section is based on a fixed helical pitch and a constant elliptical cross section may be formed. 32 a free or project free of projections and a long-lasting direction. The inventors have found that the process of manufacturing can be found in a common bend radius. Thus, the process of the inner tube is a relatively rapid and inexpensive process.

Once the inner tube 32 is formed, it is assembled with the outer tube 30, by inserting the inner tube 32 inside the outer tube. such a loose fit or a slight interference fit. Thus, the inner tube 32 and the outer tube 30 may be assembled by hand or automated. 36 of the outer tube 32 may then be carried out. This is a non-de-formed end section 32a and 32b of the inner tube.

[0021] FIG. 5c shows a cross sectional view, in the direction of arrows A-A shown in Fig. 3a, of the internal heat exchanger 11, and illustrated the inner tube 30 once assembled. The can be seen from the figure, the inner tube 32 is an approximate ellipse; B.C. 18mm. It will be a cross section of the inner tube. As an ellipse, as is illustrated in Fig. 5a could be used. Other examples could include a triangular or quadrilateral shape as illustrated in Fig. 5b could also be used. Indeed, other cross sectional profiles may be contemplated, which have increased numbers of sides.

In this example shown in FIG. 5c, the inner tube 32 contacts the inner surface of the outer tube 30 at points 56a and 56b, thus forming the two outer tubes of the outer tube 30 32. The fluid flow channels 52a. The fluid flow channels 52a. The fluid flow channels 52a. and 52b carry liquid side refrigerant. 52a and 52b may be permitted. The extent of this permit may be dependent upon the application. A third refrigerant fluid flow channel 50 is the third refrigerant flow channel 50. 32c of the inner tube 32c.

The third refrigerant fluid flow channel 50 has a cross sectional area which is equal to, or is only marginally reduced by the cross sectional area. suction side, low pressure lines of the air conditioning system 1, are made. This is a low-pressure line 21. By avoiding (a) loss of efficiency in the operation of the air conditioning system;

In addition, the inventory is surprisingly discovered by the flow tube 32 does not cause a significant drop in pressure in the fluid flow channel 50 with no helical structure. The surprising lack of pressure drop in the suction side of the internal heat exchanger 11

Whilst in the application of the internal heat exchanger 11, the present invention is designed to be useful in the field. other applications of greater pressure drop may be permitted. This may be for example, 2%, 5% or 7% increase with a helical profile with no helical structure. However, in the case of certain applications, the suction side pressure drop per unit of the internal heat exchanger can be up to 30% higher than the normal suction side line. In other embodiments this figure may be 10% or 20%.

It will be appreciated that in certain known heat exchangers, it may be appreciated. One of the reasons for this is that it is not easy to change the problem. For example, it may not be possible to change the cross-sectional area of the channel due to space constraints or bending constraints. Additionally, this may be due to the fact that there is an increase in the need for operations. Additionally, it may not be possible to change the characteristics of the device.

As can be see from Fig. 5c, the area of the inner tube; 52a and 52b is the increase of the flow channel of the refrigerantfluid flow channels. The Flow Flow Channels 52a and 52b are roughly crescent shaped, with a low height of the height of the inner tube. of flow flow channels 52a by line 58 in the figure. It will be appreciated that the flow of fluid flow channels 52a and 52b flows; and a large amount of heat exchange channels 52a and 52b.

[0028] FIG. 6 illustrates the flow of refrigerant in the internal heat exchanger. The refrigerant flowing in the refrigerant flow channel is also referenced 62a and 62b, respectively. Factors of the Fluid Flow in a Flow Flow Channel 50

It will be understood that different applications will vary. , The heattransfersurface of the present may be varied. Clearly, the exterior dimensions, such as the length and diameter of the space. 32 may be varied as is illustrated in Fig. 7. FIG. 7 illustrates part of the image of Fig. 4 illustrating several deformed portions 44 of the inner tube 32; "a" = width of the base form, determined by the material or; "b" = height of base form: "c" = "distance between symmetry axis of two deformations"; = length of straight portion of the base form, which is zero if the form is elliptical.

32. The parameters "a", "b" and "f" determine the cross-section of the liquid flow channels 52a and 52b and therefore the flow velocity and heat transfer coefficient. The parameters "c" and "e" determine heat exchange surface. In general: (c) and "e"; B.C. by increasing the number of deformations per unit of the tube 32 and decreasing the slope of the helix; this may be in the range of 20 to 45 degrees for example; (ii) "c" and "e"; B.C. by decreasing the number of deformations per unit of the tube 32 and increasing the slope of the helix; this may be in the range of 45 to 90 degrees for example.

It will be appreciated that if the internal heat exchanger 11 is to be formed, it should be a good bending stability. The bending stability of the internal heat exchanger 11 may be increased by the value of the parameter "f.

It will be understood that the above-mentioned embodiments give rise to certain advantages. 32 is the heat of the inner tube. outer tube 30, and this may be a clamp, or process used. This is provided by flexibility in terms or manufacturing. Heat exchanger applications with different performance criteria. The inner tube maybe made from low-cost material. No expensive extrusions are required and no suction side connection is needed, which may be a problem. Bending flexibility of the deformed tube. The outer tube 30 may be used as a connection sleeve. Despite the fact that the low-pressure channel may be too large, it is relatively small.

It will also be understood that the above described embodiments. For example, a "same direction" implementation. Additionally, the refrigerant used in the above described embodiments is R-134a, other refrigerants could equally be used. For example, other low pressure refrigerants or refrigerants that work at high pressures, such as carbon dioxide. Moreover, it is appreciated that it will be appreciated. These may include, for example, busses, lorries, trains and non-mobile applications. Additionally, cross sections could be used, such as elliptical cross sections.

[0034] Theid description has been presented only to illustrate and describe the present invention. It is not intended to be exhaustive or limited to invention. It will be a good idea of the invention. In addition, many modifications may be made to the scope of the invention. Therefore, it is intended to be the only means of enforcement of the claims. The invention may be in the form of a practice or not. The application is limited to the following claims.

Claims 1. The heat exchanger of the outer conduit and the outer conduit, the inner conduit and the outer conduit being the outer surface of the outer conduit and the outer surface of the outer conduit, with a cross sectional form of the outer conduit, the outer conduit of the inner conduit, the area of the outer conduit; located at a first angular position in a plane, and (ii) a corresponding region of increased outerdimension of the inner conduit at a second angular position in the plane, perpendicular to the axial length of the outer dimension; 2. A heat exchanger according to the requirements of the outer conduit. in the plan of the outer conduit, which is oval (non-circular ellipse), triangular or quadrilateral, providing two, three or four fluid flow channels, respectively, outer conduit and the inner conduit. 3. The heat exchanger according to claim 1 or 2 is a cross sectional form of the fluid flow channel. 4. The heat exchanger according to any of claims 1 to 3, which is the heat exchanger of the fluid flow channel. 5. The heat exchanger according to any of claims 1 to 4; 6. The heat exchanger according to any of claims 1 to 5, where the deformations are nonoverlapping. 7. The heat exchanger according to one of claims 1 to 5 8. The heat exchanger according to any of the requirements of the outside refrigerant conduit, including the length of the outer refrigerant conduit, -deformed conduit so that the pressure drop caused by the unit is the same as in the case of the non-deformed conduit. 9. The method of manufacturing the heat exchanger of the outer conduit, the method is: locally deforming the inner conduit at a plurality of positions distributed along its axial length, such that the external dimension of the inner conduit is reduced; close up of the outer conduit and the outer conduit and the outer surface of the outer conduit and the outer surface of the outer conduit ,. \ twhich has been the subject of an internal conduit. \ t second angular position in the plane, and the progressive rotation of the axial length of the axial length; follows a helical path along the longitudinal axis of the outer conduit .. 10. A me thod according to claim 9; 11. A method according to claim 9; 12. A method according to any one of claims 9 to 11, which is a tube of a circular cross section. 13. The method according to any one of the claims 9 to 12, which is one of the most important aspects of the present invention. 14. A method according to any of the claims, wherein the helix of the inner refrigerant is manufactured by means of a cross-sectional shape; longitudinal axis of the tube; deforming the tube, rotating the tube, rotating the tube, rotating the tube by steps of 45 °, deforming the tube a new position along the longitudinal axis with the new fixed angle; 15. A method for making any of the claims 9 to 14;

Dissertation 1. Wärmetauscher umfassend meals with dumplings and meals Innovations of the angiordnet, wobei die innere Leitung und die äußere Leitung angeordnet you, e e Fluidströmungskanal zwischen der inneren Fläche der äußeren Leitung und der äußeren Fläche der inneren Leitung zu bilden, wobei der Fluidströmungskanal eine Querschnittsform in einer zur Längsachse der äußeren Leitung im Wesentlichen senkrechten Ebene aufweist, , dass die innere Leitung mehrere zonen aufweist, die entlang ihreraxialen Western hernia, wobei jede Zone (i) Bereich mit verringerter Äußerer Abmessung der inneren Leitung, der in einer ersten Winkelstellung in einer zu ihreraxialen West im Wesentlichen senkrechten Ebene liegt, und (ii) einen entsprechenden Bereich mit vergrößerter Ausserer Dimension der inneren Leitung in einer zweiten Winkelstellung in einer zu ihreraxialen Länge im Wesentlichen senkrechten Ebene umfasst, wobei der Bereich mit verringerter Ausserer Dimension dem Fluidströmungskanal entspricht und der Bereich mit vergrößerter Ausserer Abmessung einer For contact with the patient, the patient is in contact with the Spiralform entanglement of the Längsachse der äußeren Leitung angeordnet. 2. Wärmetauscher nach Anspruch 1, wobei die innere Leitung derart verformt ist, dass sie eine Querschnittsform in einer zur Längsachse der äußeren Leitung im Wesentlichen senkrechten Ebene aufweist, die im Wesentlichen oval (nicht-greiförmige Ellipse), dreieckig oder sveteckig ist, vorausgesetzt, jeweils zwei, drei oder Vier Fluidströmungskanäle sind jeweils durch zwei, drei oder Vier Contact us about the Leitung getrennt. 3. Wärmetauscher nach Anspruch 1 or 2, wobei die Querschnittsform des Fluidströmungskanals im Wesentlichen sichelförmig ist. 4. Wärmetauscher nach einem der Ansprüche 1 bis 3, wobei der Teu der äußeren Fläche der inneren Leitung, der den Fluidströmungskanal definiert, eu im Wesentlichen convex Fläche zum Inneren des Fluidströmungskanals aufweist. 5. Wärmetauscher nach einem der Ansprüche 1 bis 4, wobei die Verformungen separate Verformungen sind. 6. Wärmetauscher nach einem der Ansprüche 1 bis 5, wobei die Verformungen sich nicht überlagern. 7. Wärmetauscher nach einem der Ansprüche 1 bis 5, wobei die Verformungen entlang der Längsachse der inneren Leitung durchgehend you. 8. Wärmetauscher nach einem der Ansprüche 1-7, wobei die innere Tongschlung en llg der Länge der äußeren, e. Inneren Teeth of the verursacht wird, im Wesentlichen derselbe ist wie der Druckabfall der entsprechenden nicht verformten Leitung oder bezüglich diesem nicht deutlich vergrößert ist. 9. Verfahren zum Herstellen Eine Wärmetauschers umfassend eine äußere leitung und eine innere Leitung, an inner cord, Wigei das Verfahren Folgendes umfasst: locales , i.e. dass in jeder Position of the abmessung der inneren Leitung verringert ist;

Zusammenbauen der verformten inneren Leitung mitderäußeren Leitung, dass die innere Leitung im Wesentlichen mindestens zwei Linienberührungen mit der äußeren Winkelstellung in einer zu ihrer axialen Winkelstellung in einer zu ihrer West im Wesentlichen senkrechten Ebene vergrößert wird, und progressives Drehen des inneren Rohrs bezüglich des Verformungsvorgangs, wenn sich die innere Leitung in den mehreren Positionen entlang ihrer axialen Western verformt, ie dass der Fluidströmungskanal in dem zusa mmengebauten Wärmetauscher einem schraubenförmigen Weg entlang der Längsachse der äußeren Leitung folgt. 10. Verfahren nach Anspruch 9, wobei der Verformungsvorgang in jeder der mehreren Positionen ein separater Vorgang, wie zum Beispiel ein Klemmoder ein Einschlagvorgang, ist. 11. Verfahren nach Anspruch 9, wobei der Verformungsvorgang in jeder der mehreren positionen ein durchgehender Verformungsprozess, wie zum Beispiel Walzen, ist. 12. Verfahren nach einem der Ansprüche 9 bis 11, Wigei das Grundleitungsmaterial ein Rohr mit im Wesentlichen, Chief Marshal of Querschnitt. 13. Verfahren nach einem der Ansprüche 9 bis 12, wobei der Verformungsvorgang ein oder mehrere profierte Verderungselemente verwendet, die die innere Leitung mit einem ovalen, dreieckigen odervierecki-gen Querschnittsprofil zu versehen. 14. Verfahren nach einem der Ansprüche 9 bis 13; Bilden, vorzugsweise Klemmen oder or Hämmern, des fixierten Rohrs, m e n e n g in Verformung des Rohrs zu schaffen, Drehen des Rohrs et al. neuen Position entlang der Längsachse mit dem neuen fixierten Winkel und Wiederholen dieses Schritts, bis die gewünschte Schraubener Spiralform geschaffen wird, hergestellt wird. 15. Verfahren nach einem der Ansprüche 9 bis, wobei das Bilden durch Verwenden einer Biegemaschine, Biegeradius von Null eingestellt ist, automatisiert wird.

Revendications 1. Echangeurde chaleur comprenant une conduite extérieure et al. la surface intérieure de la conduite extérieure de la conduite de la condéite de la coupé transversale, dans and plan sensiblement perpendiculaire à l'axe longitudinal de la conduite extérieure, qui est allongée sensiblement plus grande dans la direction circonférentielle de la conduite extérieure que dans la direction radiale de la conduite extérieure, de la conduite de la conduite de la pluralité de pluralité de la ré de la de la de la de la longueur axiale au niveau desquelles la conduite intérieure est déformée localement, chaque zone comprenant ( i) une région de dimension extérieur (ii) une région correspondence de dimension extérieure augmentée de la conduite intérieure en une seconde position de la conduite intérieure située à une premiere axiale, la-dio de dimension extenrieure diminuée correspondant au canal d'écoulement fluids de la résidence de extenrieure augmentée correspondant à and point de contact d'en déeurée des lière et en ete en ete en en et le que le le etal le le de lée d'etoulement fluidique est agencé selon une forme hélicoïdale le long de l'axe longitudinal de la conduite extérieure. 2. Echangeurde chaleur selon la revendication 1, dans lequel la conduite en déformée de façon à avoir une forme en coupe transversale, dans and plan sensiblement perpendiculaire à l'axe longitudinal de la conduite extérieure (ellipse non circulaire) , triangulaire ou quadrilatérale, fournissant respectivement deux, trois ou quatre canaux d'écoulement fluidique separé para de deux, trois ou quatre points de contact entre la conduite extérieure et la conduite intérieure. 3. Echangeur de chaleur selon la revendication ou 2, dans lequel la forme en coupe transversale du canal d’écoulement fluidique est sensiblement en croissant. 4. Echangeur de chaleur selon l quelconque des revendications 1 à 3, dans lequel la partie de la surface extérieure de la conduite intérieure définissant le canal d’écoulementfluidique présente une surface sensiblement convexe vers l'intérieur du canal d’écoulement fluidique. 5. Echangeur de chaleur selon l quelconque des revendications 1 à 4, dans lequel les déformations sont des déformations discrètes. 6. Echangeur de chaleur selon l'quelconque des revendications 1 à 5, dans lequel les déformations sont non chevauchantes. 7. Echangeur de chaleur selon l quelconque des revendications 1 à 5, dans lequel les déformations sont continues le long de l'axe longitudinal de la conduite. 8. Echangeur de chaleur selon l'une quelconque des revendications 1 à 7, dans lequel la conduite de la conduite de fluide de la liqueur de la conduite de la flué de liqueur, concend une aire en coupe transversale qui est sensiblement heaale à, ou n'est que atmosèrement réduite par rapport aune conduite de déformée de valte que la chute de pressio de la feu de la conde de la condéite de la feu de la feu de la chêtre de la chêté de la chême que, ou non augmentée de façon significative for rapport à la chute de pression de la conduite non déformée équivalente. 9. Procédé de fabrication d'unchangeur de chaleur comprenant une conduite extérieure en une conduite intérieure agencée à l'intérieur et le long de l'axe longitudinal de la conduite extérieure, la procéé de la condée de la conduite intérieure à une pluralité de positions répartie le long de sa longueur axiale, de sorte qu'à chaque position la dimension extérieure de la conduite intérieure te réduite; l'assemblage de la conduite en déformée avec la conduite extérieure de la que la conduite de la condéite de la condiite de la condiite de la condiite de la conduite de la conduite deux canaux d'écoulement. de la condéite de la condéite de la condéite de la condéite de la condéite de la condéite de la condéite de la condéite de la condéite de la condaite de la conduite de la conduite de la conduite de la première à la résué à la prère de la première position angulaire dans un plan sensiblement perpendiculaire à sa longueur axiale, et la dimension extérieure de la conduite intérieure en augmentée une seconde position angulaire dans and plan sensiblement perpendiculaire à sa longueur axiale, et la rotation progressive du tube intérieur on rapport à léopération de déformation à mesure que la conduite intérieure est défo rmée à la pluralité de poste le long de sa longueur axiale de flué de dans l'é changeur de chaleur assemblé suiv and chemin hélicoïdal le long de l'axe longitudinal de la conduite extérieure. 10. Procédé selon la revendication 9, dans lequel l'opération de déformation à chacune de la pluralité de positiones un une opération discrète, tel. 11. Procédé selon la revendication 9, dans lequel l'opération de déformation à chacune de la pluralité de positions est and process de deformation continu tel que le laminage. 12. Procédé selon l'ie quelconque des revendications 9 à 11 dans lequel le matériau de conduite de base est and tube de coupe transversale sensiblement circulaire. 13. Procédé selon l'e quelconque des revendications 9 à 12, dans lequel l'opération de déformation utilis and ou plusieurs de déformation prof. De la déire de conduite intérieure d’un profil en coupe transversale ovale, triangulaire ou quadrilatérale. 14. Procédé selon l'une quelconque des revendications 9 à 13, dans lequel la forme hélicoïdale de la conduite de la feu de la feu de la la fédéré de feu de la la fédération d'un tube avec une forme en coupe transversale donnée, de préférence une forme circulaire, à and angle fixe dans une direction donnée de l'axe longitudinal du tube; le formage, but fuss le le serrage ou le calage, du tube fixe afin de créer une déformation locale du tube, la rotation du tube à la carte de de longitudinal, de la résidence la rotation du tube par étapes de 45 °, la déformation du tube à une nouvelle position le long de l'axe longitudinal avec le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le le léeuvre, lé de l'hôtel. 15. Procédé selon l'e quelconque des revendications 9 à 14, dans lequel le formage est automatisé par l'utilisation d'une machine à cintrer réglée à and rayon de courbure nul.

REFERENCES CITED IN THE DESCRIPTION

This is a list of references for the reader. It does not form part of the European patent document. Even though they have been taken in compiling the references, errors or omissions cannot be ruled out.

Patent documents cited in the description • DE 102006017816 B4 [0002] · US 4194560 A

Claims (9)

THERMAL EXCHANGE PATTERN WPPbfaK 1, · Heat exchanger, which includes an external conductor, and an inner conductor located in the outer conduit and along its longitudinal axis, which is arranged to form a fluid flow channel on the inner surface of the outer conduit. and between the outer surface of the inner conduit, the cross-section of the fusion flow channel being oblong in a plane approximately perpendicular to the longitudinal axis of the outer conduit, such that the circumference of the outer conduit in the direction of the direction is greater than in the radial direction of the outer conduit, characterized in that it has an axial length axial length for the outer conduit : distributed over several zones: where the inner conductor is deformed locally, each of which includes (i) a first angular position in a plane approximately perpendicular to the axial length of the inner conductor area, heat! the outer diameter of the inner conductor is reduced, and (also) an area in the second angle position corresponding to the axial length of the inner conductor, in which the outer diameter of the inner conductor is increased, the reduced outer area corresponding to the flux flow channel and wherein the enlarged outer area corresponds to a point of contact between the inner and outer conduits, and that the i'-lumen channel is arranged in a spiral along the longitudinal axis of the outer conduit; 2, The heat exchanger according to claim X, wherein the inner conductor is deformed so that its cross-section is substantially oval (non-circular ellipse), triangular or rectangular in a plane substantially perpendicular to the longitudinal axis of the outer conduit, thereby providing two, three, or four tubular flow channels. which are separated by three, four or four points of contact between the outer and inner conductors, 3, Az. or a heat exchanger according to claim 2, wherein the cross-section of the flushing channel is substantially sickle-shaped. 4, X'3. The heat exchanger according to any one of claims 1 to 4, wherein the portion of the inner conduit defining the floid flow channel has a hump surface substantially facing the inside of the hid flow. A heat exchanger according to any one of claims 1 to 4, wherein the deformations are non-coherent deformations. 6, The heat exchanger according to any one of claims 5 to 5, wherein the deformations do not overlap '7th THE? Heat exchanger according to any one of claims 1-4, wherein the deflector wads are continuous along the longitudinal axis of the inner conductor. 8. Aíi 1-7. The heat exchanger according to any one of claims 1 to 3, wherein the internal refrigerant line comprises a cross-sectional area * along the length of the external refrigerant conductor, which is approximately equal to, or slightly smaller than, an equivalent, non-deformed conductor so that the internal refrigerant line is a unit the pressure drop caused by the length of the length is about the same as the pressure drop of the equivalent, non-deformed wire, or in a larger stall, A method of heat exchanger heat exchanger% comprising an outer conductor and an inner conductor disposed within the outer conduit and its longitudinal axis, and comprising:; locally deforming the inner conductor in a plurality of locations distributed along the axial length so that the outer diameter of the inner conductor is reduced at each location; assembling the deformed inner conductor with the outer conduit such that the inner conductor has at least two line contacts between the outer conductor and the outer surface of the outer conductor and the inner surface of the inner conductor; to form a fluidized-bed ducting channel, characterized in that the deformation molding is carried out on the inner conductor so that the outer conduit of the inner conduit at each location; be in a plane approximately perpendicular to the axial length of the inner conductor, a first angular clearance is reduced, and the outer dimension of the inner conductor is one, the inner conductor; in an axially longitudinal plane approximately perpendicular to the first sleeve: softened, and gradually rotated, the inner tube is formed for the deformation operation | as in the plurality of locations along the axial length defornplpdlkv that the ilu flow flow in the assembled heat exchanger is the longitudinal axis of the outer conduit! to form a spiral path, li. A method according to claim 9, in which the deformation step at each location is a separate operation, such as a split or blow! operation. 11, &amp; '· 9. The method of claim 1 wherein m is a deformation operation performed in a manner which is a continuous deformation process, such as rolling. 12, A 9-11. The method according to any one of claims 1 to 3, wherein the base wire material is a method according to any one of the preceding claims, wherein the deformation! In operation, one or more shaped deformation elements are used to provide the inner conductor with an oval, triangular or rectangular body profile. 14, A 9-13. A method according to any one of claims 1 to 3, wherein the spiral shape of the internal refrigerant line is produced by forming a plurality of saberberries, which have been inoculated in a given direction of the vessel, in a particular cross-sectional shape, preferably a circular cross-sectional tube; Elite's Mama and Mate's Mate or Hail the Garbage Gun to Come to the Oeo Local OefanTillahalah Gets the Behind The Behind The Behind The Behind Themselves: é $ f mé® $ k rb # drank | eaogbm eiooyóe yao oouvoo 45 -os lábebeti jáli iaiaia, deform the tube bosoctenpelyo: along ggy new baip in the ya rog exposed exposed legends, eat the: litpisá aoklg ki not form the desired: caavatYoal or spiral shape, Ü, A 9 -14, The shape of the pseudopods of the request is driven by a nourishment with zero Ibouta spf.