WO2005075913A1

WO2005075913A1 - Device for heat exchange and method for producing one such device

Info

Publication number: WO2005075913A1
Application number: PCT/EP2005/001032
Authority: WO
Inventors: Gerrit WÖLK
Original assignee: Behr Gmbh & Co. Kg
Priority date: 2004-02-04
Filing date: 2005-02-02
Publication date: 2005-08-18
Also published as: DE102004005621A1; US20080035305A1; EP1716377A1

Abstract

The invention relates to a device for heat exchange, said device comprising a flow device and a collection and/or distribution device connected to the flow device at a connection point. The flow device has a pre-determined length and a flat tubular cross-section, and a fluid under a high pressure, for example an operating pressure of approximately 125 bar, flows through the same. Said flow device has a linear course over the entire length thereof, along a longitudinal axis thereof. The long side of the flat tubular cross-section of the flow device is approximately between 5 mm and 6.1 mm, and is at an angle of approximately 90°, at the connection point, in relation to a main direction of extension of the collection and/or distribution device.

Description

_ f _

BEHR GmbH & Co. KG. Mauserstrasse 3, 70469 Stuttgart

Heat exchange device and method of making such a device

The present invention relates to a heat exchanger for a high-pressure cooling circuit, in particular to a high-pressure cooler, in particular a high-pressure gas cooler, and / or high-pressure auxiliary heater.

In the following, a high-pressure cooling circuit is to be understood as a cooling circuit in which a fluid flowing through the cooling circuit, at least in sections, under an operating pressure of approximately 110 bar to 130 bar, in particular approximately 125 bar. and / or which cooling circuit must be designed for burst pressures in a range from 270 bar to 360 bar according to applicable safety regulations.

Such heat exchangers in high-pressure cooling circuits, hereinafter referred to as high-pressure heat exchangers for short, are known from the prior art.

10 shows a section of such a, in this case double-row, high-pressure heat exchanger or double-row high-pressure gas cooler from the prior art.

In the two-row high-pressure heat exchanger or high-pressure gas cooler in the prior art, tubes 1000 are arranged in two parallel planes. The tubes arranged in one plane are also aligned parallel to each other.

BESTATIGUNGSKOPIE In the prior art, the tubes 1000 have a flat tube-like shape which has a long side 1002 in cross section 1001 and a side 1003 which is considerably shorter than this long side 1002.

A coolant flows through the (flat) tube 1000 in a longitudinal direction 1004, for which purpose a plurality of flow channels 1005 are generally provided in the flat tube 1000, essentially parallel to the longitudinal direction 1004 or to a longitudinal axis of the flat tube 1000.

The coolant is at least in this section under an operating pressure of approximately 125 bar. According to the applicable safety regulations, the high-pressure heat exchanger or high-pressure gas cooler is designed for burst pressures in the range from 270 bar to 360 bar.

In end sections 1009 at both ends 1008 of the flat tube 1000, the flat tube 1000 according to the prior art each has a continuous twist or twist (torsion) about its longitudinal axis up to 90 °.

Both ends 1007 of the flat tube 1000 in the prior art which are rotated by 90 ° in this way are connected to collection and / or distribution devices 1008 in the manner of hollow bodies in a liquid-tight and / or gas-tight manner.

A connection with one another is understood to mean a connection in such a way that a liquid and / or gaseous fluid, such as, for example, the coolant, can flow in a liquid-tight and / or gas-tight manner through this connection.

At a connection point between one end of the flat tube 1000 and the hollow body-like collecting and / or distributing device 1008, the long side 1002 of the cross section 1001 of the flat tube 1000 runs essentially parallel to a longitudinal axis (main direction of expansion) of the hollow body-like collecting and / or distributing device 1008. Due to the rotation of the flat tube ends 1007, measurement of the hollow body-like collection and / or distribution device 1008, ie an inner cross section of the hollow body-like collection and / or distribution device 1008, and thus a material thickness can be reduced. As a result, the bursting pressures required in accordance with the safety regulations and the prevailing operating pressures with reduced material thicknesses and material expenditures can be achieved for the hollow body-like collection and / or distribution device 1008.

However, the rotation of the flat tube ends 1007 disadvantageously reduces a surface of the flat tube 1000 that can be used for heat exchange, in particular for cooling, and thus an end face of the high-pressure heat exchanger that can be used for cooling.

In addition, the rotation of the flat tube ends 1007 disadvantageously restricts a free choice of a distance 1010 in the parallel spacing 1010 of the flat tubes 1000 from one another. A minimum height of a fin fin in the heat exchanger or gas cooler is thereby limited.

The twisting of the flat tube ends 1007 also disadvantageously limits a transverse division of a heat exchanger matrix of the gas cooler.

The twisting of the flat tube ends 1007 also increases the manufacturing costs that are required to produce the flat tubes.

Corresponding or correspondingly disadvantageous also applies in particular to high-pressure auxiliary heaters known from the prior art and also to high-pressure heat exchangers known from the prior art in general.

The object of the present invention is therefore to provide a high-pressure heat exchanger which is less expensive to produce than the prior art and less restrictive in its geometry even with small material thicknesses. This is achieved according to the invention by the device for exchanging heat and by the method for producing a device for exchanging heat with the features according to the respective independent patent claim.

Advantageous embodiments and further developments are the subject of the dependent claims.

The inventive device for exchanging heat has at least one throughflow device and at least one collection and / or distribution device connected to the at least one throughflow device at a connection point.

A connection is understood to mean a connection such that a liquid and / or gaseous fluid, such as a coolant, in particular carbon dioxide, is liquid and / or gas-tight under high pressure, for example an operating pressure of approximately 110 bar to 130 bar, especially of approximately 125 bar.

The flow device according to the invention has a predetermined length (flow device length) and a flat tube-like cross section.

In the context of the invention, a flat tube-like cross section (flat tube) is understood to mean a cross-sectional shape which has a long side (depth) and a side which is considerably shorter than this long side (height).

A fluid under a high pressure, for example an operating pressure of approximately 110 bar to 130 bar, in particular approximately 125 bar, can flow through the flow device and the collection and / or distribution device. The flow device according to the invention has a straight course along the entire flow device length along a longitudinal axis of the flow device.

A straight course along the longitudinal axis is understood to mean a course in which the throughflow device or the flat tube-like cross section of the throughflow device is neither twisted, twisted or twisted about the longitudinal axis nor does the longitudinal axis itself have a curved or curved course.

The long side of the flat tube-like cross section of the flow device, hereinafter also referred to as the (flow device) depth, has a length of approximately 5 mm to 6.1 mm, in particular of 5 mm to 5.9 mm.

At the connection point, the long side of the flat tube-like cross section of the flow device has an angle of approximately 90 ° with respect to a main direction of expansion of the collection and / or distribution device.

The device according to the invention for heat exchange or the flow device according to the invention is based on the non-trivial finding that with cross-sectional depths of the flow device of approximately 5 mm to 6.1 mm, in particular of 5 mm to 5.9 mm, cross-section twists at the ends of the flow device are dispensed with can.

If the now straight flow device is connected to a collection and / or distribution device in such a way that the long side of the flat tube-like cross section of the flow device has an angle of approximately 90 ° with respect to the main direction of expansion of the collection and / or distribution device, with the The device according to the invention achieves or achieves bursting pressures above the required 270 bar even with reduced material thicknesses and / or it can also be operated with reduced material thicknesses in a high pressure range. In the method for producing a device for exchanging heat, a connection is made at a connection point between at least one flow device and at least one collection and / or distribution device, which connection is taken from a group, which soldered, welded or adhesive connections contains.

The at least one throughflow device is preferably inserted and / or soldered into the at least one collecting and / or distributing device.

A connection is understood to mean a connection in such a way that a liquid and / or gaseous fluid, such as a coolant, can flow liquid-tight and / or gas-tight under high pressure, such as an operating pressure of approximately 125 bar, through this connection.

The flow device and the collection and / or distribution device have the specifications mentioned above.

Precisely due to the elimination of the cross-sectional rotation of the flow device, hereinafter referred to as tube twist or flat tube twist, which is possible with the invention, these and the embodiments and further developments have these advantages in the high pressure region.

The straight flow device according to the invention can thus be used to achieve a larger, finned end surface which is relevant for heat exchange than in a comparable, twisted flow device.

Also, in the case of a parallel arrangement of a plurality of flow devices according to the invention, in particular (flat) tubes, no minimum distance between two of the flow devices must be maintained in one plane. Corrugated fins between adjacent flow devices with lower overall heights can thus be realized. Furthermore, the flow devices to be used for the production of flow devices according to the invention are lower than in comparable, twisted flow devices.

Likewise, the invention results in a lower use of material and consequently lower material costs in comparison to conventional multi-row heat exchangers.

Handling of the straight flow-through devices in the manufacture of high-pressure heat exchangers, in particular high-pressure coolers and / or high-pressure auxiliary heaters, and there in particular in the case of a pipe feed for a cassette, is also simplified.

In addition, geometrically simpler collection and / or distribution devices, which are connected to the untwisted ends of the flow devices, can be implemented.

In a preferred embodiment, the flow device, for example a flat tube, has a height or cross-sectional height of approximately 1 mm to 2 mm and / or a length of approximately 200 mm to 800 mm. Below the height is the one above, opposite the long side, i.e. to understand the depth, much shorter side of the flat tube-like cross section. An internal passage height of a channel within the flat tube is preferably between 0.4 mm and 1 mm.

In a further preferred embodiment, the flow-through device has at least one inner flow channel essentially parallel to the longitudinal axis of the flow-through device, preferably a plurality of inner flow channels essentially parallel to the longitudinal axis.

In cross section, the at least one flow channel can have a shape that is essentially circular or elliptical, polygonal or rectangular, or has mixed forms thereof, for example rectangular with more or less rounded corners. The at least one flow channel is flowed through at least in sections by a medium (fluid), such as a coolant, which is capable of flow, at an operating pressure of approximately 125 bar.

In the context of the invention, flowable media or fluids are understood to mean liquid and / or gaseous media of any viscosity, such as, in particular, but not exclusively, oils, liquids, in particular high heat of vaporization, water, air or gases, for example carbon dioxide, and refrigerants which evaporate or condense can. The flowable media can also contain additives, for example to inhibit corrosion.

At the connection point, the collection and / or distribution device can provide a recess for connecting the flow device. A cross section of the recess is adapted to the flat tube-like cross section of the flow device. In addition, the recess can have additional shapes, which serve, for example, as an insertion bevel for flat tubes.

In a further preferred embodiment, the collection and / or distribution device has a tubular cross section. Preferably, an inner diameter of the tubular cross section of the collection and / or distribution device is approximately equal to the (cross section) depth of the flow device.

The device according to the invention is particularly suitable for a high-pressure heat exchanger, in particular a high-pressure cooler, in particular a high-pressure gas cooler, and / or a high-pressure auxiliary heater.

Such a heat exchanger has a plurality, as a rule a multiplicity, of flow devices according to the invention, such as flat tubes, which are arranged in at least one plane, essentially parallel to one another and at a predeterminable distance. Ribs or corrugated ribs, preferably in series, can be arranged between two adjacent flow devices. A corrugated fin height can be approximately 2 mm to 8 mm. The corrugated fins of one plane can also be separate corrugated fins.

Alternatively, a corrugated fin that is continuous over several levels can be provided.

In the case of the heat exchanger, the plurality of flow devices are furthermore connected at least at one end at a connection point to a collection and / or distribution device in an essentially gas-tight and / or liquid-tight manner.

The plurality of flow-through devices are preferably arranged in two levels, the ends of the flow-through devices being connected in one plane to a collecting and / or distributing device.

In a further embodiment, the flow devices of two adjacent levels can also be offset from one another.

In a further preferred embodiment, a cooler and / or an auxiliary heater according to the above heat exchanger, the fins are each arranged between two adjacent flow devices, for example between adjacent flat tubes. A coolant under high pressure flows through the plurality of flat tubes, a heat exchange between the coolant and an air surrounding the plurality of flat tubes being promoted.

A further preferred embodiment, a device for air conditioning an air conducted into a vehicle interior of a motor vehicle, has at least one compressor, a heater and / or evaporator according to the above preferred embodiment, an expansion valve and a cooler according to the above embodiment. The compressor and the expansion valve are known from St. It is also known that in high-pressure cooling circuits, the coolant is under high pressure at least in a section of the cooling circuit which extends from an outlet of the compressor via the high-pressure heat exchanger to the expansion valve.

Further advantages and embodiments of the present invention will become apparent from the accompanying drawings. In it show:

Figure 1 is a partial view of an inventive device for exchanging heat, a heat exchanger of a gas cooler. FIG. 2 is a diagram which shows a relationship between the geometric dimensions of components of a device for exchanging heat, a heat exchanger of a gas cooler, according to the invention;

3 shows a graph with a relationship between a block depth of a two-row gas cooler with flat tubes according to the invention and a flat tube depth of a tube according to the invention for two burst pressures;

4 shows a graph with a relationship between a flat tube depth of a tube according to the invention and a block depth of a two-row gas cooler with flat tubes according to the invention for two burst pressures;

Fig. 5 is a graphical representation with a relationship between an air flow velocity and a gas cooler output for a gas cooler with flat tubes according to the invention and for a comparable Gas cooler with twisted flat tubes most gas cooler matrix;

6 shows a graphical representation with a relationship between an air flow velocity and a gas cooler output for a gas cooler with flat tubes according to the invention and for a comparable gas cooler with twisted flat tubes according to a second gas cooler matrix;

7 shows a graph with a relationship between a flat tube width and a weight of a gas cooler matrix for different gas cooler matrices;

8 shows a graphical representation with a relationship between an air flow velocity and a weight-related gas cooler output for a gas cooler with flat tubes according to the invention and for a comparable gas cooler with twisted flat tubes according to a first gas cooler matrix;

9 shows a graphical representation with a relationship between an air flow velocity and a weight-related gas cooler output for a gas cooler with flat tubes according to the invention and for a comparable gas cooler with twisted flat tubes according to a second gas cooler matrix; Fig. 10 is a partial view of a conventional heat exchanger of a gas cooler with several conventional twisted flat tubes according to the prior art.

1 shows a section of a two-row high-pressure gas cooler, or gas cooler, 110. The two-row gas cooler 110 according to the embodiment has a circuit from 29/31 to 31/29 and an overall dimension of a heat exchanger matrix of approximately W x H = 462.0 x 660 mm 2. A block depth of the two-row gas cooler 110 is approximately 16 mm.

In FIG. 1, reference numeral 100 relates in each case to a (flat) tube of the two-row gas cooler 110 according to the invention.

The flat tube 100 has a tube length of approximately 670 mm and a flat tube-like cross section 101 with a long side, a flat tube depth of 5.8 mm and a side which is considerably shorter than this long side and a flat tube width of 1.5 mm.

Furthermore, the flat pipe 100 has a straight pipe run along the entire pipe length along a pipe longitudinal axis.

In the embodiment of the two-row gas cooler, the tubes 100 are arranged in two planes 102, 103 which are parallel to one another.

Within each plane 102, 103, the flat tubes 100 are also arranged parallel to one another at a distance of approximately 2 mm to 10 mm, preferably between 4 mm and 8 mm and in particular of approximately 6 mm.

Corrugated fins 106, each with a corrugated fin height of approximately 6 mm, are arranged along the pipe length or in the longitudinal direction 104 of the pipes 100 between two parallel flat tubes 100 arranged in parallel in a plane 102, 103.

The two-row gas cooler 110 according to the embodiment has a total fin density of 75 fins / dm. A preferred range for the rib density is from 65 to 85 ribs / dm.

The flat tubes 100 are flowed through by a coolant under high pressure in the longitudinal direction 104, for which purpose a plurality of flow channels 105 are provided in the flat tube 100, essentially parallel to the longitudinal direction 104 or the longitudinal axis of the flat tube 100. A pair of header tanks 120, having two header tubes 123, 124, are connected to each flat tube end 121 at a designated connection point to extend in one direction, a main direction of expansion, perpendicular to the longitudinal direction 104 of each tube 100. The coolant also flows through these under high pressure.

Accordingly, the flat tube-like cross section 101 or the long side of the flat tube-like cross section 101 of the tube 100 has a predetermined angle of approximately 90 ° at the respective connection point with respect to the main direction of expansion of the collecting tanks 120.

At the connection point, a recess for the connection of the flat tube 100 is provided on the part of the collecting tanks 120. A cross section of the recess is adapted to the cross section 101 of the flat tube 100. In addition, the recess has an additional shape, an insertion bevel for the flat tubes 100.

A connection with one another is understood to mean a connection in such a way that a liquid and / or gaseous fluid, such as the coolant in this case, can flow liquid and / or gas-tight through this connection.

Corresponding methods for producing such a tight connection, such as soldering, welding and / or gluing or combinations thereof, are known from the prior art.

The collecting tanks 120 and the collecting pipes 123, 1124 each have a tubular cross section 122, an inner diameter 200 of the tubular cross section 122 being approximately equal to the pipe depth of the flat pipe 100. A collecting pipe wall thickness 201 is dependent on a required burst pressure.

Fig. 2 shows geometric relationships for determining the block depth.

The block depth T (Ges) is determined according to: T (Ges) = 2 * T (FI) + 2 xd (wall, manifold) + b (gap),

where T (FI) denotes the flat tube depth, d (wall, manifold) a wall thickness of a manifold and d (gap) denotes a gap between the two manifolds.

3 shows a graphic representation with a relationship between a block depth of a two-row gas cooler with flat tubes according to the invention and a flat tube depth of a flat tube according to the invention for two bursting pressures, namely 270 bar and 360 bar.

The graphic relationship shown is also based on the fact that b (gap) = 0.8 mm and d (wall, manifold)

d (wall, manifold) = 0.1 * P (burst) * T (FI) / (2 * s)

determined, where P (burst) denotes the burst pressure and s a yield strength of a header pipe material, s is assumed to be 50N / mm2 (AA 3003 mod) in the present case.

Fig. 3 shows that for a block depth of 16 mm and a burst pressure of 270 bar, the maximum flat tube depth T (Fl) = 5.9 mm. At a burst pressure of 360 bar, the maximum flat tube depth T (FI) = 5.5 mm. ^'

The flat tube depth T (Fl) <6 mm for straight flat tubes in double-row high-pressure gas coolers with a block depth of 16 mm is therefore sufficient for a bursting pressure of 270 bar.

It must also be taken into account here that the depth of the flat tube decreases

T (FL) reduces a contact area between a corrugated fin and the flat tube at a constant block depth. For this reason, one should

Block depth of 16 mm the individual flat tube depth also not less than be about 5 mm. The same must also be taken into account for other companies.

Fig. 3 also shows that with a block depth of 14 mm for double-row gas coolers, the flat tube depth T (FI) <5.20 mm is sufficient for a burst pressure of 270 bar with straight flat tubes.

FIG. 4 shows a graph with a relationship between a flat tube depth of a tube according to the invention and a block depth of a two-row gas cooler with flat tubes according to the invention for two bursting pressures, namely 270 bar and 360 bar.

Fig. 4 shows, for example, that with a burst pressure of 270 bar (360 bar) and a block depth of 15 mm, a flat tube depth of approximately 5.2 mm (5.6 mm) is sufficient for straight flat tubes.

Fig. 5 and Fig. 6 show a gas cooler performance over an air flow velocity under given boundary conditions.

In. Fig. 5, two double-row high-pressure gas coolers with a fin density of 75 fins / dm, a fin height of 6 mm, a block depth of 16 mm and the same pipe connection 29/31 - 31/29 are compared.

Gas cooler 1 has conventional flat tubes with twisted flat tube ends and with a flat tube depth of 7 mm. The dimensions of the heat exchanger matrix of this gas cooler 1 are W x H = 462.0 x 650.0 mm2 with an end face F (St) = 30.0 dm2.

Gas cooler 2 has the flat tubes according to the invention with a straight tube run and with a flat tube depth of 5.8 mm. The dimensions of the heat exchanger matrix of the gas cooler 2 are W x H = 462.0 x 664.0 mm2 with an end face of 30.7 dm2.

Due to the larger end face of the gas cooler 2, the disadvantage of the smaller flat tube depth and thus reduced contact area between the corrugated fin and the flat tube can be approximately equalized. The gas cooler 2 has a nem same mass flow on a higher refrigerant side.

In Fig. 6, two double-row high-pressure gas coolers with a fin density of 75 fins / dm, a fin height of 4.5 mm, a block depth of 16 mm and the same pipe connection 37/40 - 40/37 are compared.

Gas cooler 1 has conventional flat tubes with twisted flat tube ends and with a flat tube depth of 7 mm. The dimensions of the heat exchanger matrix of this gas cooler 1 are W x H = 458.8 x 650.0 mm2 with an end face F (St) = 29.8 dm2.

Gas cooler 2 has the flat pipes according to the invention with a straight pipe run and with a flat pipe depth of 5.8 mm. The dimensions of the heat exchanger matrix of the gas cooler 2 are W x H = 458.0 x 664.0 mm2 with an end face of 30.5 dm2.

Due to the larger end face of the gas cooler 2, the disadvantage of the smaller flat tube depth and thus reduced contact area between the corrugated fin and the flat tube can be approximately equalized. The gas cooler 2 has a higher refrigerant-side pressure drop for the same mass flow.

FIG. 7 shows a graphical representation with a relationship between a flat tube width and a weight of a gas cooler matrix for different gas cooler matrices.

7 shows the relationships for a flat tube according to the invention with a flat tube depth of T (FI) <6 mm and for a conventional flat tube with a larger flat tube depth, namely T (FI) = 7 mm.

The relationships are shown ^' for the flat tube widths of 1, 4 mm and 1, 6 mm and two corrugated fin heights of 4.5 mm and 6 mm with a fin density of 75 fins / dm. A corrugated fin thickness is 0.1 mm. Fig. 7 shows a significantly lower weight for gas coolers according to the flat tube depth T (FI) <6 mm.

Fig. 8 and Fig. 9 show a weight-related gas cooler performance, which is obtained by dividing the gas cooler performance by the weight of the heat exchanger matrix, over the air inflow velocity under given boundary conditions.

The gas cooler performance shown relates to the gas coolers already discussed in Fig. 5 and Fig. 6.

Fig. 8 and Fig. 9 show that the weight-related gas cooler output for the two gas coolers with the flat tubes according to the invention with a flat tube depth T (FI) <6.1 mm is significantly greater compared to the two gas coolers with conventional flat tubes with a flat tube depth of 7 mm.

The present invention can be applied in particular to coolers or auxiliary heaters of a high-pressure cooling circuit. An embodiment of the respective heat exchanger matrix is not limited to the geometries described above. It can be chosen arbitrarily within the scope of the inventive flat tube geometry and the burst pressure requirements.

Although the present invention has been fully explained in connection with preferred embodiments with reference to the accompanying drawings, numerous modifications and modifications will occur to those skilled in the art, all of which are within the scope of the present invention as defined in the appended claims.

Claims

Patent claims

1. Device for exchanging heat, with at least one flow device and at least one collection and / or distribution device connected to the at least one flow device at a connection point, wherein the at least one flow device has a flat tube-like cross section with a long side and a short side opposite the long side Side and a predetermined flow device length, wherein the at least one flow device and the at least one collection and / or distribution device can be flowed through by a fluid under a high pressure, characterized in that the at least one flow device along a longitudinal axis along the entire flow device length of the flow device has a straight course, the long side of the flat tube-like cross section has a length of approximately 5 mm to 6.1 mm, in particular 5 mm to 5.9 mm, and the long side at the connection point Side of the flat tube-like cross section of the flow device has an angle of approximately 90 ° with respect to a main direction of expansion of the collecting and / or distributing device.

2. Device according to claim 1, characterized in that the short side of the flat tube-like cross section of the flow device has a length of approximately 1 mm to 2 mm and / that the flow device length is approximately 200 mm to 800 mm.

3. Device according to at least one of the preceding claims, characterized in that the flow device has at least one inner flow channel essentially parallel to the longitudinal axis, preferably a plurality of inner flow channels essentially parallel to the longitudinal axis.

4. Device according to the preceding claim, characterized in that the at least one flow channel has a cross-sectional shape that is essentially circular, elliptical, polygonal or rectangular, or mixed forms thereof.

5. The device according to at least one of the preceding claims, characterized in that the device has a plurality of the flow devices, each of which is connected to the at least one collection and / or distribution device and / or which is essentially in at least one plane and / or are arranged substantially parallel to each other.

Device according to the preceding claim, characterized in that the plurality of flow devices are arranged in two levels.

7. Device according to the preceding claim, characterized in that the device has two collection and / or distribution devices, each of which is connected to one end of the at least one flow device.

8. Device according to one of the preceding claims, characterized in that the at least one collecting and / or distributing device has a tubular cross section, an inner diameter of the tubular cross section of the collecting and / or distributing device tion is approximately equal to the long side of the flat tube section of the flow device.

9. Device according to one of the preceding claims, characterized in that the fluid flowing through the at least one collecting and / or distributing device is a coolant and / or is under a pressure of approximately 125 bar.

10. Cooler, in particular gas cooler, and / or auxiliary heater with a device according to one of the preceding claims, characterized in that the cooler and / or auxiliary heater has a plurality of the flow devices, each of which is connected to the at least one collection and / or distribution device and / or which are arranged essentially in one plane and / or substantially parallel to one another, and the cooler and / or auxiliary heater has a plurality of ribs which are arranged between adjacent flow devices substantially perpendicular to the longitudinal direction of the respective flow device by a Promote heat exchange between air and the fluid.

11. Device for air conditioning an air conducted into a vehicle interior of a motor vehicle, with at least one compressor, an evaporator and / or auxiliary heater, an expansion valve and a cooler, at least one auxiliary heater and / or one cooler according to claim 10.

12. A method for producing a device for exchanging heat, characterized in that in the method at a connection point between at least one flow device and a collection and / or distribution device a connection is established, which connection a Group is removed, which contains soldering, welding oc fertilize, the at least one flow device

has a flat tube-like cross section with a long side with a length of approximately 5 mm to 6.1 mm, in particular 5.9 mm, and with a side that is short compared to the long side,

has a predetermined flow device length,

- A high-pressure fluid can flow through and - A straight line runs over the entire flow device length along a longitudinal axis of the flow device, the at least one collection and / or distribution device through which the high-pressure fluid can flow, and at the connection point the long side of the flat tube-like

Cross-section of the flow device has an angle of approximately 90 ° with respect to a main direction of expansion of the collecting and / or distributing device.