EP2225523A1

EP2225523A1 - Modular heat exchange system

Info

Publication number: EP2225523A1
Application number: EP08863394A
Authority: EP
Inventors: Franz Summerer
Original assignee: A-Heat Allied Heat Exchange Technology AG Germany
Current assignee: A-Heat Allied Heat Exchange Technology AG Germany
Priority date: 2007-12-18
Filing date: 2008-10-16
Publication date: 2010-09-08
Also published as: BRPI0821238A2; ES2369815T3; WO2009077225A1; RU2010129958A; CA2709578A1; JP2011506902A; AU2008337808A1; US20100282439A1; CN101903732A

Abstract

The invention relates to a modular heat exchange system (1) comprising a heat exchange module (2, 21, 22). At least one first heat exchange module (21) of said heat exchange system (1) has a heat exchanger (3). An external boundary of the heat exchange module (2) is formed by an inflow surface (4) and a discharge surface (5) in such a way that a transport fluid (6) can be fed to the heat exchange module (2) via the inflow surface (4), can be brought into fluid contact with the heat exchanger (3), and can be discharged again from the heat exchange module (2) via the discharge surface (5) in order for heat to be exchanged between said transport fluid (6) and a heating medium (7) that flows through the heat exchanger (3) in the operating state. According to the invention, a first boundary surface (81) of the first heat exchange module (2, 21) is inclined by a predefined angle of inclination (α) relative to a second boundary surface (82) of the first heat exchange module (2, 21).

Description

Modular heat exchange system

The invention relates to a modular heat exchange system with a heat exchange module according to the preamble of independent claim 1.

The use of heat exchange systems is well known in a number of prior art applications. Heat exchangers are used in refrigerators, e.g. used in ordinary household refrigerators, in air conditioners for buildings or in vehicles of all kinds, especially in automobiles, aircraft and ships, as water or oil coolers in internal combustion engines, as condensers or evaporators in coolant circuits and in a myriad of different applications, all of which are well known to those skilled in the art are.

There are different ways to classify heat exchangers from different applications. One attempt is to make a distinction according to the design of the various types of heat exchangers. Thus, a classification according to so-called "laminated heat exchangers" on the one hand, and "Minnichannel-" or "Microchannelwärmetauscher" on the other hand be made.

The laminated heat exchangers, well known for a very long time, serve, like all types of heat exchangers, to transfer heat between two media, for example, but not only, to transfer from a cooling medium to air or vice versa, as is known, for example, from a classic household refrigerator in which heat is released to the ambient air via the heat exchanger for generating a cooling capacity in the interior of the refrigerator.

The ambient medium outside the heat exchanger, e.g. Water, oil or often simply the ambient air, which absorbs heat or transfers heat to the heat exchanger, for example, is either cooled or heated accordingly. The second medium may e.g. be a liquid refrigerant or heat transfer or a vaporizing or condensing refrigerant. In any case, the surrounding medium, e.g. the air, a much lower heat transfer coefficient than the second medium, e.g. the coolant that circulates in the heat exchanger system. This is compensated by greatly different heat transfer surfaces for the two media: The medium with the high heat transfer coefficient flows in the tube, which on the outside by thin sheets (ribs, fins) has a greatly enlarged surface at which the heat transfer, for. takes place with the air.

Fig. 3 shows a simple example of an element of such a known laminated heat exchanger. In practice, the

Heat exchanger thereby formed by a plurality of such elements according to FIG. The ratio of the outer surface to the inner surface depends on the Lamellengeomethe (= pipe diameter, pipe arrangement and pipe spacing), and from the fin spacing. The lamellar spacing is chosen differently for different applications. However, purely thermodynamically, it should be as small as possible, but not so small that the air-side pressure loss is too large. An economic optimum is about 2mm, which is a typical value for condenser and recooler.

The production of these so-called laminated heat exchangers is carried out according to a long-known standardized process: The slats are punched with a press and a special tool and in

Packages laid out to each other. Subsequently, the tubes are inserted and expanded either mechanically or hydraulically so that a very good contact and thus a good heat transfer between the tube and lamella arises. The individual tubes are then connected together by arches and manifold and manifold, often soldered together.

The efficiency is essentially determined by the fact that the heat that is transferred between the fin surface and the air, must be transmitted through heat conduction through the fins to the pipe. This heat transfer is more effective, the higher the conductivity or the thickness of the lamella, but also the smaller the distance between the

Pipes is. This is called the lamella efficiency. As a lamellar material is therefore nowadays predominantly aluminum used, which has a high thermal conductivity (about 220 W / mK) to economic conditions. The pipe pitch should be as small as possible, but this leads to the problem that you need many pipes. Many pipes mean high costs because the pipes (usually made of copper) are considerably more expensive than the thin aluminum fins. This material could be reduced by reducing the pipe diameter and the wall thickness, ie you build a heat exchanger with many small pipes instead of few big pipes. Thermodynamically, this solution would be optimal: very many tubes in close proximity with small diameters. However, a significant cost factor is also the working time for expanding and soldering the pipes. This would increase extremely with such a geometry.

Therefore, a few years ago, a new class of heat exchangers, so-called minichannel or microchannel heat exchangers, have been developed, which are manufactured by a completely different process and almost correspond to the ideal of a laminated heat exchanger: many small tubes with small spacings.

Instead of small tubes, however, the mini-channel heat exchanger

Used aluminum extrusions, the very many small channels with a diameter of e.g. about 1 mm. Such an extruded profile, which is also known per se, is known e.g. shown schematically in Fig. 2. In practice, a heat exchanger, depending on the required heat output, already manage with a single extruded profile as a central heat exchange element. Of course, in order to achieve higher heat transfer rates, it is also possible to provide simultaneously in a single heat exchanger a plurality of extruded sections which are interconnected in suitable combinations, for example by means of connections and discharges, e.g. be soldered together.

Such profiles can e.g. be made easily and in a variety of forms from a variety of materials in suitable extrusion. However, other methods of making minichannel heat exchangers are known, such as e.g. the assembly of suitably shaped profile sheets or other suitable methods.

You can not do these profiles and you do not need to widen them and they will not be pushed into stamped plate packs. Instead For example, be placed between two closely spaced profiles (common distances, for example, <1 cm) sheet metal strips, especially aluminum sheet strips, so that by alternating juxtaposition of sheet metal strip and profile a heat exchanger package is created. This package is then completely soldered in a soldering oven.

Due to the narrow distances and the small channel diameter, a heat exchanger with a very high fin efficiency and a very small filling volume (channel inside) is created. The other advantages of this technique are the avoidance of material pairings (corrosion), the low weight (no copper), the high pressure stability (about 100 bar) and the compact design (typical depth of a heat exchanger, for example 20mm).

In mobile use, mini-channel heat exchangers have established themselves during the 1990s. The low weight, the small block depth and the limited dimensions that are required here are the ideal conditions for this. Car coolers and condensers and evaporators for car air conditioning systems are today almost exclusively realized with mini-channel heat exchangers.

In the stationary area, on the one hand, larger heat exchangers are usually needed; on the other hand, the emphasis here is less on weight and compactness than on the optimal price-performance ratio. Minichannelwärmeaustauscher were previously limited in size to be eligible. Many small modules would have to be connected consuming. In addition, the use of aluminum in the extruded profiles is relatively high, so that hardly a cost advantage was expected from the use of materials.

Due to the high quantities in the automotive sector, the production processes for mini-channel heat exchangers have become standardized and improved, so that today this technology can be described as mature. The size of the soldering furnace has meanwhile also increased, so that heat exchangers in the size of 6 can already be made of about 1 x 2 m. The initial difficulties with the connection system are resolved. There are now several patented procedures how the stiffening and header pipes can be soldered.

Above all, however, the price of copper, which has risen sharply in comparison with aluminum, is now causing this technology to become very interesting for stationary use as well.

In addition to the simple systems in which essentially only one surrounding medium, such as air, is available for exchanging heat, so-called hybrid coolers or hybrid dry coolers are also known, as disclosed, for example, in WO90 / 15299 or EP 428647 B1 are, in which the gaseous or liquid medium of the primary cooling circuit to be cooled flows through a lamella heat exchanger, and deliver the dissipated heat through the cooling fins partly as sensitive and partly as latent heat to the air flow. One or more fans promote the flow of air through the heat exchanger and advantageously have variable speed. The dissipation of the latent heat is carried out by a liquid medium, preferably water, which is adapted to its specific values such as conductivity, hardness, content of carbonates and each is applied as a drop-forming liquid film on the air side heat transfer surface. Immediately below the heat exchanger elements, the excess water drips back into a collection tray. Also sprayed heat exchanger concepts are known where water is sprayed on the finned heat exchanger and completely evaporated and the evaporation energy is used to improve the heat transfer as well as in the wetting for energy optimization. Here you can drive without excess water, but a deposit formation must be prevented, for which, for example, deionized water is used. It is understood that in special cases other than water, other cooling fluids, such as oil in question.

The operation of wetting or spraying the fins of the heat exchanger results in significant energy and water savings compared to conventional methods, such as open cooling towers.

A disadvantage, however, is the restriction of the choice of material of the wetted or sprayed heat exchanger tube in connection with the lamella, where it must not come in conjunction with an electrolyte to corrosion.

Hybrid heat transfer is thus understood to mean the considerable improvement in the heat transfer of fin heat exchangers with pipes by targeted wetting or spraying of water. In this case, it is especially necessary to regulate the air velocity in the disk pack in such a way that the water titration on the disk surface does not occur. This is advantageously achieved by a speed control of the fans or by other suitable measures.

The disadvantage here is that the sprayed or wetting water acts together with dissolved ions as the electrolyte, which can lead to numerous corrosion problems in the usually used material pairings copper pipe, and aluminum fins of the heat exchanger.

As a suitable surface protection for heat exchangers, it is known, for. B. to use the so-called cataphoretic dip coating. Furthermore, both the material pairings such as copper tube and lamella, as well as aluminum tube and lamella and stainless steel tube and lamella are used to control the problem of contact corrosion. It is also known to completely galvanize the heat exchanger. To the quality of the circulation or

Spray water is subject to high demands in terms of pH, water hardness, chlorine content, conductivity, etc., in order to prevent that on the one hand deposits on thickening on the lamella by evaporation, and on the other hand form too high levels of chemically reactive substances, which in turn can lead to corrosion together with the deposits.

To achieve higher heat transfer rates than e.g. in small heat exchangers from the automotive or household technology are known, has been used in larger heat transfer systems so far to resort to the hybrid technology described above.

Another way of obtaining greater heat transfer performance is, in principle, by combining several individual heat exchange components, e.g. through the interconnection of AI-MCHX modules, attempts to achieve greater exchange rates.

A problem with all previously known heat exchange systems, however, is that an existing heat exchange system either not at all or only with very great difficulty, that is ultimately only with great effort and considerable costs in his

Heat transfer performance can be adjusted. That goes for one

Increase, as well as for a reduction of the heat transfer performance of an existing system.

These known difficulties are due to various reasons.

The known heat transfer systems are usually self-contained devices whose heat transfer performance can be regulated at best within certain narrow limits by, for example, the

Flow rate of a refrigerant is regulated by the heat exchanger, or the amount of the cooling medium, eg of cooling air through the regulation the suction power of a fan is varied. It is also possible, for example, to reduce the amount of cooling air in that the heat exchanger has adjustable Luftabschottklappen, thereby the flow rate of cooling air, which is supplied to the heat exchanger, is adjustable.

However, by all these known measures, the performance of a heat exchange system can only be varied between zero and a maximum heat exchange rate. An increase in the heat transfer capacity over a system-related maximum value addition is not possible.

Also, it is usually not possible, or in particular for economic and / or technical reasons not possible or not useful to make the heat transfer performance of an existing heat exchange system arbitrarily small, or to reduce to zero. That is, the known heat transfer systems must always be operated with a certain minimum heat transfer performance, which often makes the operation unnecessarily inefficient, but can not be avoided.

So, for example, if the heat transfer performance of an existing heat exchange system to be lowered efficiently, for example, because the size of an associated cold store was significantly reduced, so far usually no other option than the existing

Heat exchange system to replace another with correspondingly lower performance.

Conversely, if the heat transfer performance of an existing heat exchange system to be significantly increased, for example, an associated cold store must be massively increased, usually remains for this case in practice often no other economical alternative than the existing heat transfer system by a system with higher To replace heat transfer performance. The heat transfer performance of existing systems can therefore not be increased in a simple manner, that is, above all, economically from an economic point of view. Purely constructive, a known heat transfer system with given heat transfer performance, for example, not just an additional

Heat exchangers are added. Additional heat exchangers can not be simply mounted in or on the existing housing constructions and can be connected into the existing cooling circuits.

Even where that under difficulties under purely geometric

In principle, such an extension would be so technically complex that such a change is not worthwhile.

Of course, one way to increase the heat transfer performance of an existing system is to install a second additional system. But again, in practice, new problems arise that often do not allow such a solution.

In fact, it is not easy to integrate an additional heat exchange system into the existing control electronics. First, such control systems are technically simply not designed to drive another heat exchange system, so additional control electronics must be installed. If, however, then both heat exchange systems, for example, must be operated simultaneously for cooling one and the same enlarged cold store, the coordination of the two independent control systems is at least very difficult. In many cases, especially if, for example, frequent and / or large changes in the cooling power to be provided are necessary, reliable coordination of the control systems becomes impossible. In many cases, however, for example, even for reasons of space, the installation of an additional heat transfer system is not possible.

This may be due, for example, to the fact that it is not possible to install additional control electronics and / or additional cooling circuits with the necessary refrigeration machines and the other components known per se in the given spatial conditions on site. But also the additional installation of the known bulky heat exchange modules, which contain as central elements the heat exchangers, for example in the form of laminated and / or in the form of micro-channel heat exchangers, is frequently not only possible for reasons of space or not desirable or simply too expensive technically and economically.

This means, in the end, that one does not achieve the necessary power density in an extended heat exchange system, because the extension of an existing heat exchange system by additional

Heat exchange modules already for purely geometric reasons can not be made sufficiently compact.

Moreover, the question of the lack of power density of the known heat exchange systems is in many areas a generally unsolved problem. Especially where in a small space a large amount of heat must be transmitted in the shortest possible time, for example in large electronic systems, such as in very powerful data processing systems, or other systems known in the art, the power densities of known heat exchange systems are often not sufficient , The only solution is then often, the

Install heat exchange modules with the heat exchangers in a remote location where there is enough space for the under-compacts Heat exchange modules is, with all known technical and economic disadvantages.

The object of the invention is therefore to provide an improved heat exchange system which overcomes the problems known from the prior art and with which, in particular, high cooling capacities in a minimal space, ie higher power densities in heat transfer, can be achieved by a compact design. On the other hand, at the same time a heat exchange system will be provided, the heat transfer performance is very flexible in a technically simple and economically efficient manner easily changeable, that is both in very wide limits both can be increased, as well as reducible.

The objects of the invention solving these objects are characterized by the features of independent claim 1.

The dependent claims relate to particularly advantageous embodiments of the invention.

The invention thus relates to a modular heat exchange system with a heat exchange module comprising at least a first heat exchange module with a heat exchanger. In this case, an outer boundary of the heat exchange module is formed by an inflow and an outflow surface such that for exchanging heat between a Transportfluidum and a heat exchanger flowing through the heat exchanger in the operating state, the Transportfluidum supplied via the inflow to the heat exchange module, can be brought into flowing contact with the heat exchanger and can be discharged again via the outflow surface from the heat exchange module. According to the invention, a first boundary surface of the first heat exchange module with respect to a second boundary surface of the first heat exchange module inclined at a predetermined inclination angle.

Essential to the invention is thus that in a modular heat exchange system of the present invention, a first boundary surface of a first heat exchange module with respect to a second boundary surface of the first heat exchange module is inclined at a predetermined inclination angle.

By suitable choice of the angle of inclination, which is particularly preferably not equal to 90 °, the invention thus provides a modular heat exchange system which, depending on the design, can be extended substantially periodically or not periodically in one, two or three spatial dimensions by stringing together preferably identical heat exchange modules , or even reducible, by simply removing one or more heat exchange modules from an existing system.

The appropriate choice of the angle of inclination, or the concrete choice of the mutually inclined surfaces determines decisively whether a periodic expansion in one, two or three dimensions is possible, or determines the maximum number of heat exchange modules, which are modular according to the invention Have the heat exchange system assembled.

For example, if the shape of the heat exchange module, the external shape of a triangular prism selected with an angle of 60 °, so a maximum of six heat exchange modules of this kind can be combined into a highly compact heat exchange system of hexagonal structure, which have a very high power density in terms of heat transfer. With such a hexagonal heat exchange system consisting of six heat exchange modules, heat exchange performance due to new requirements can be reduced, so that the necessary number of heat exchange modules can be easily removed from the hexagonal heat exchange system.

If, in another case, the heat exchange modules are formed, for example, in the form of a parallelepiped having an inclination angle of 45 °, two such heat exchange modules can each be provided in a particularly compact manner, e.g. be assembled over the inclined surfaces and also, if necessary, be expanded by stringing together.

Thus, the heat transfer performance and / or heat transfer performance of a modular heat transfer system of the present invention can be easily and efficiently adjusted by regularly repeating preferably identical heat exchange modules or by removing identical heat exchange modules.

Thus, in a particularly preferred embodiment, the first boundary surface of the first heat exchange module is inclined with respect to the second boundary surface of the first heat exchange module at the predeterminable angle of inclination, that the modular

Heat exchange system can be expanded by a second heat exchange module, in particular in a compact design, wherein the second heat exchange module is preferably identical to the first heat exchange module. Compact design means that two heat exchange modules can be combined as possible to save space, so that between two combined heat exchange modules as little, preferably practically no free space remains

In a particularly simple, particularly compact and therefore cost-effective design, the heat exchanger itself has a load-bearing Function in the formation of the heat exchange module. This can for example be realized in that the heat exchanger itself forms a housing wall of the heat exchanger module, or that the housing of the heat exchanger module does not have a boundary wall at all boundary surfaces of the housing, so that the heat exchanger itself performs a connecting and stabilizing integral function as a housing component.

As mentioned, a particularly important importance to those inventive embodiments in which the heat exchange system is formed of a plurality of heat exchange modules, as in these, for example, by removing a

Heat exchange module particularly easy heat transfer performance is reduced.

Advantageously, the angle of inclination between the first boundary surface and the second boundary surface of the heat exchange module is between 0 ° and 180 °, more particularly between 20 ° and 70 °, preferably between 40 ° and 50 °, and most preferably the angle of inclination is 45 ° and / or the angle of inclination is between 90 ° and 180 °, in particular at 120 °.

In a specific embodiment of the present invention, to form a heat exchange system in the form of a heat exchange cluster, the angle of inclination between the first boundary surface and the second boundary surface of the heat exchange module is 3607n, where n is an integer, and the heat exchange cluster is preferably a number of n identical heat exchange modules is formed, for example, to form a hexagonal heat exchange cluster, the angle of inclination between the first boundary surface and the second boundary surface of the heat exchange module is 60 °, the hexagonal heat exchange cluster to achieve a maximum heat exchange performance and / or a maximum power density of Heat exchange is preferably formed from six identical heat exchange modules. In a further simple embodiment, a boundary surface of the heat exchange system can be missing on the housing, wherein the missing housing wall is formed in the installed state of the heat exchange system by a wall of an installation object, in particular by a wall of a building is formed.

To further increase the power density of the heat transfer between the heating medium and the transport fluid and / or to increase a heat transfer rate between the heating medium and the transport fluid, a cooling device may be provided for cooling the heat exchanger, in particular a fan for generating a gas flow, and / or the heat exchange system as known per se and described in detail as a hybrid system, and it can be a sprinkler for sprinkling the heat exchanger with a cooling fluid, in particular with cooling water formed. A droplet separator for separating the cooling fluid is also particularly advantageous.

In this case, the heat exchanger itself, as known from the prior art, by a plurality of microchannels as a microchannel heat exchanger and / or the heat exchanger may also be formed as a laminated heat exchanger with cooling fins. Specifically, the heat exchange system is formed as a combination heat exchange system of the laminated heat exchanger and the microchannel heat exchanger, if specific requirements favor such a design.

To improve the possibilities to regulate the heat transfer performance of a heat exchange system according to the invention, for example, a foreclosure, in particular a Luftabschottung for regulating a flow rate of the transport fluid may be provided, which can be controlled either manually or via a drive unit in response to a predetermined operating parameters and / or regulated.

Very advantageously, a compensating means known per se can be provided to compensate for thermo-mechanical stresses. The components of the modular heat exchange system of the present invention, such as the heat exchangers and / or a supply and / or discharge for the heating means and / or any other component of a heat exchange system according to the invention with any other component of the heat exchange system by a

Universal connection element may be connected so that, for example, a heat exchange module can be added or removed particularly easily. Specifically, more preferably, the manifolds and headers for the heaters or even blues and other modules and components of the heat exchanger system are connected to a universal connector. These universal connecting elements are particularly well suited for both vertical and horizontal installation of the heat exchange systems or the heat exchange modules.

In addition, a cleaning system may further be provided, comprising in particular a dust trap and / or a scraper and / or a dishwasher, in particular a cleaning opening and / or a cleaning flap, so that the heat exchange system, or its components such as the heat exchange module or other components simple and can be cleaned efficiently. In addition to other possible embodiments, the heat exchanger can be provided, for example, on the cleaning flap and / or the heat exchanger itself can be designed as a cleaning flap.

For control and / or regulation of the heat exchange system in the operating state, is usually, but not necessarily, a drive unit, in particular a drive unit with a data processing system for controlling the cooling device and / or the cleaning system and / or Luftabschottung and / or an operating or Condition parameter of the heating means and / or another operating parameter of the heat exchange system may be provided, as it is known per se from the prior art in existing heat exchange systems to those skilled in the art. The heat exchange system or the heat exchange module and / or the heat exchanger and / or a boundary surface of the heat exchange module, in particular the entire heat exchange system is particularly advantageously made of a metal and / or a metal alloy, in particular a single metal or a single metal alloy, and in particular made of stainless steel, in particular made of aluminum or an aluminum alloy, wherein a sacrificial metal is preferably provided as corrosion protection, and / or wherein the heat exchange system is at least partially provided with a protective layer, in particular with a corrosion protection layer. Especially the distribution and header pipes are preferred for high pressures, for example, for operation with CO ₂ , made of high-strength materials such as stainless steel.

In particular, a heat exchange system according to the invention is a radiator, in particular a radiator for a vehicle, in particular for a land vehicle, for an aircraft or for a watercraft, or a radiator, a condenser or an evaporator for a mobile or stationary heating system, cooling system or air conditioning in particular a cooler device for a machine, a data processing system or for a building or for another device which is to be operated with a heat exchange system.

In the following the invention will be explained in more detail with reference to the drawing. In a schematic representation:

1 shows a first embodiment of a heat exchange system according to the invention;

FIG. 2 shows a heat exchanger according to FIG. 1 with microchannels; FIG.

3 shows an element of a laminated heat exchanger; Fig. 4 shows a second embodiment according to FIG. 1 with

Air partitioning;

Fig. 5a shows a third embodiment according to FIG. 1 with

Cleanout;

Fig. 5b, the embodiment of Fig. 5a during a

Cleaning process;

Fig. 6a another embodiment of an inventive

Heat exchange system with universal connector;

FIG. 6b a universal connecting element of FIG. 6 in detail; FIG.

Fig. 7 shows a heat exchange system with two

Heat exchange modules;

Fig. 8a shows a first known heat exchange system for vertical installation operation;

8b shows a second known heat exchange system for operation in horizontal installation;

9 shows a heat exchange system according to the invention for operation in vertical installation;

FIG. 10 shows a heat exchange system according to the invention for operation in horizontal installation; FIG.

11 shows another heat exchange system of four

Heat exchange modules; Fig. 12 shows a first embodiment of a heat exchange cluster in hexagonal form;

FIG. 13 shows a second embodiment according to FIG. 12; FIG.

FIG. 14 shows another embodiment of a heat flow dam cluster. FIG.

1 shows a schematic representation of a first simple exemplary embodiment of a heat exchange system according to the invention, which in the following is provided overall with the reference numeral 1.

The inventive heat exchange system 1 of Fig. 1 comprises as an essential element, a heat exchange module 2, 21 with a

Heat exchanger 2 for exchanging heat between a heating means 7, e.g. a cooling liquid 7 or an evaporating agent 7 and a transporting fluid 6, e.g. Air 6. The heat exchanger 3 is in the present case, a per se known microchannel heat exchanger 3 with a plurality of microchannels 10. The heat exchanger 3 is with its microchannels 10 via a not shown in Fig. 1 connection system, which is known in the art in principle, for Exchange of heating means 7 connected to a chiller, also not shown.

In a manner known per se, the chiller is connected to the connection system, comprising an inlet channel with an inlet segment of the inlet

Heat exchanger 3 and an outlet channel with an outlet segment of the heat exchanger 3, connected in such a way that the heat means 7 for exchanging heat with the air 6 from the inlet channel via the inlet segment, through the plurality of microchannels 10 of the heat exchanger 3, and finally via the outlet segment of the outlet channel can be fed. An outer boundary of the heat exchange module 2 is formed by an inflow 4 and an outflow 5 such that in the operating state for exchanging heat between the Transportfluidum 6, whose flow direction is shown symbolically by the arrows 6, and the heat exchanger 3 by flowing heat means 7, the

Transport fluid 6 can be supplied via the inflow surface 4 to the heat exchange module 2, can be brought into flowing contact with the heat exchanger 3 and can be discharged again via the outflow surface 5 from the heat exchange module 2.

In order that the heat between the air 6 and the heating means 7 can be better exchanged, there is additionally provided a cooling device 9, in the present case a ventilator 9, with which an amount of air 6 which is conveyed through the heat exchange module 2, 21 per unit time, is controllable.

Here, the first boundary surface 81, which is formed in the present case by the heat exchanger 3 itself, the heat exchange module 2, 21 with respect to a second boundary surface 82, 83 of the first heat exchange module 2, 21 at a predetermined inclination angle α, in the present specific example about 35 °, inclined. It is understood that in another embodiment, the inclination angle α may also have a different value, e.g. a value greater than or less than 35 °, for example, but not limited to, 25 ° or 45 °. In the case of the simple exemplary embodiment according to FIG. 1, the second boundary surface 82, 83 is formed by a wall 800 of an installation object, which in the present case is a cold store (not shown).

In Fig. 2, a heat exchanger 3 according to FIG. 1 with micro channels 10 is shown schematically in section. Instead of small tubes, as used in the classic laminated heat exchangers 3 as shown in FIG. 3, are, as already mentioned, used in Minichannelwärmetauschern 3 eg aluminum extruded profiles, which have a lot of small channels 10 with a diameter of eg about 1 mm. The heat exchanger 6 of FIG. 2 can be made, for example, in a suitable extrusion process, simply and in a variety of forms from a variety of materials. In this case, the heat exchanger 3 according to FIG. 2 can be produced in another embodiment variant not explicitly illustrated in FIG. 2, also by other production methods, such as, for example, by the assembly of suitably shaped profile sheets or other suitable methods.

Fig. 3 shows, in contrast to FIG. 2, an element of a known laminated heat exchanger 3 with cooling fins 300, as it could also be used instead of a micro-channel heat exchanger 3 in an embodiment of the present invention. The heating means 7 flows through the tubular element of the laminated heat exchanger 3, which exchanges heat in the operating state mainly via the cooling fins 300 with the air 6 flowing past it. It is understood that in practice the heat exchanger 3 is usually formed from a plurality of elements according to FIG. In a very specific embodiment of the present invention, which is not shown explicitly for reasons of space with reference to a drawing, a combination heat exchanger 3 is used as a heat exchanger 3. That is, a heat exchange system 1 of the present invention may include a laminated heat exchanger 3 with cooling fins 300 for specific applications, besides a heat exchanger 3 having a plurality of microchannels 10, simultaneously.

In order to cope with possibly even greater heat transfer performance, the heat exchange system 1 can also be designed as a so-called hybrid system 1, the functional principle of which is likewise known per se to a person skilled in the art, and therefore not explicitly based on a separate system Drawing must be presented. In that case, a sprinkling device is preferably provided for sprinkling the heat exchanger 3 with an external cooling fluid, in particular with cooling water or cooling oil. In particular, a droplet separator, eg in the form of a tank for separating and collecting the external cooling fluid in the tank, can additionally be provided

Operating state be provided, so that the external cooling fluid in an external cooling system, which is used for cooling the external cooling fluid, is rezierkulierbar and re-cooling of the heat exchanger 3 this can be supplied via the sprinkler again.

4, a second simple embodiment according to FIG. 1 with an air partition 11 is shown schematically. The Luftabschottung 11 is preferably in the form of a blind or a Venetian blind comprising individual blind elements 111 and Storenelemente 111 configured so that the degree of coverage of the heat exchanger 3 is variably, preferably electronically controlled and / or controlled variable, in which the

Luftabschottung in a known manner, for example, wholly or partially by pulling together the individual shutter elements 111 and shutter elements 111 is removed from the surface of the heat exchanger 3, or by changing an angle between the individual shutter elements 111 and the surface of the heat exchanger 3, so that the effective Passage area for the air 6 is variable. As a result, in a simple way, without changing the flow dynamics in the cooling system, a regulation of the heat exchange performance of the heat exchanger 3 possible.

5a and 5b show a third exemplary embodiment according to FIG. 1 with a cleaning flap 121, FIG. 5a showing the heat exchange system 1 shortly before a cleaning process in which the interior, in particular the surface of the heat exchanger 3, is to be freed from dirt, FIG. which inevitably accumulates during operation of the heat exchange system. Fig. 5b shows the heat exchange system 1 during the cleaning process. The cleaning flap 121 is configured as an access flap 121, which is designed to be rotatable about the axis of rotation 122 according to the arrow P, so that by pivoting the cleaning flap 121 about the axis of rotation 122, which may be configured, for example, as a universal connecting element 13, access to the interior of the heat exchange system 1 is provided, which allows easy service, repair and cleaning work inside without the heat exchange system 1 must be dismantled.

FIG. 5 b shows a situation in which the heat exchanger 3 is currently being cleaned with a cleaning liquid 123, for example with water 123. The cleaning flap 121 has been pivoted on the basis of the situation of Fig. 5a so around the axis of rotation 122 that it acts according to FIG. 5b as a sump 121, which reliably collects the dirty cleaning fluid 123 during the cleaning process, so that the dirty cleaning fluid safely and possibly automatically can be removed and disposed of, so that, for example, adverse effects on the environment are avoidable.

In Fig. 6a, another embodiment of an inventive heat exchange system is shown schematically, in which the cleaning flap 121 is attached to a universal connector 13 according to FIG. 6b. The universal connection element 13 is suitable, inter alia, for simple and reliable connection of distribution and collecting pipes, which are not explicitly shown in FIGS. 6a and 6b and serve for supplying or discharging the heating means 7 to and from the heat exchanger 3 ,

Preferably, the universal connection element 13 is designed so that it is particularly simple, for example via a screw connection or by soldering with the corresponding parts of the heat exchange system 1 is connectable.

It may be suitable for connection of conduits carrying thermal means 7, or even itself as conduit for the conveyance of heating means 7. It may further be suitable for joining sheet metal parts, such as the cleaning flap 12 or other parts. In a given modular heat exchange system 1, the universal connection element 13 is preferably designed in detail such that it can simultaneously create as many different connections as possible in one and the same embodiment, so that as few differently formed universal connection elements must be used simultaneously in one and the same modular heat exchange system 1.

Ideally, the universal connector 13 is configured to simultaneously perform all connection functions between all parts of the modular heat exchange system, such that only one type of universal connection element needs to be used in the same heat exchange system 1, which is the design, extension or design Reduction of a novel modular heat exchange system 1 enormously simplified and thus guarantees maximum flexibility of the system.

Fig. 7 shows a modular heat exchange system 1 according to the present invention comprising two identical heat exchange modules 2, 21, 22. The two modules are of identical design, wherein the inclination angle α has a value of 45 °. The person skilled in the art immediately understands that, in principle, any desired number of identical heat exchange modules 2, 21, 22 can be added in both directions of the double arrow DP. That is, to change the heat exchange performance of the modular heat exchange system 1 requires only a single type of Wärmeaustauschnnodulen 2, 21, 22 ready to be provided to provide a system 1 with virtually any predeterminable heat exchange performance, or to expand this or to reduce in an existing system by reducing the number of heat exchange modules 2, 21, 22 whose heat exchange performance. Particularly preferably, the individual heat exchange modules 2, 21, 22 are integrated into the heat exchange system 1 by using the universal connection elements 13, as already discussed with reference to FIGS. 6 a and 6b.

In addition to the enormous flexibility which a heat exchange system 1 according to the invention has with regard to the number and possibilities of arrangement of the heat exchange modules 2, 21, 22, a heat exchange system 1 according to the invention is also very flexible with respect to the installation or installation direction of the heat exchange system 1.

In Fig. 8a and Fig. 8b are very schematically two known from the prior art heat exchange systems 1 'shown.

In order to better distinguish the prior art from the present invention, those features which refer to examples from the prior art are provided with an apostrophe, while the reference numerals for features according to the invention do not carry an apostrophe.

A major disadvantage of the known heat exchange systems 1 'according to FIG. 8a or FIG. 8b is that they are in relation to the direction of gravity S either only in the vertical installation direction, as shown in Fig. 8a, or only in the horizontal direction of installation Fig. 8b are usable. Here, vertical means that the outflow direction of the air 6 'from the heat exchange system 1' is substantially perpendicular with respect to the direction of gravity S, while a horizontal installation direction means that the one from the heat exchange system outflowing air 6 'flows substantially parallel or antiparallel to the direction of gravity.

Thus, the heat exchange system 1 'of Fig. 8a constructed for vertical installation can not be exchanged for the heat exchange system of Fig. 8b designed for horizontal installation only.

Again, the inventive modular heat exchange system 1 is much more flexible, as demonstrated impressively with reference to FIGS. 9 and 10.

In Fig. 9, a heat exchange system 1 comprising two heat exchange modules 2, 21, 22 in vertical installation manner, in Fig. 10, a heat exchange system 1 in a horizontal installation manner with respect to the direction of gravity S shown. The individual heat exchange modules 2, 21, 22 of the heat exchange systems according to FIG. 9 and FIG. 10 are completely identical. That is, only one type of heat exchange modules 2, 21, 22 need be provided to produce both horizontal and vertical heat exchange systems 1. In particular, it is even possible that one and the same heat exchange system 1 simultaneously comprises vertically and horizontally oriented heat exchange modules 2, 21, 22.

FIG. 11 shows by way of example a further heat exchange system 1 comprising four heat exchange modules 2, 21, 22, each with two fans 9, whereby the heat exchange capacity of the individual heat exchange modules 2, 21, 22 is substantially increased. The person skilled in the art will readily understand that the embodiment according to FIG. 11 can also be advantageously used both in the vertical and in the horizontal installation direction.

In Fig. 12, a first embodiment of a heat exchange cluster 1 in hexagonal form is further exemplified. The modular Heat exchange system 1 in the form of the heat exchange cluster 1 according to FIG. 12 comprises six identical heat exchange modules 2, 21, 22, which all have an angle of inclination of 60 °. By choosing this special geometry, it is possible to combine the six heat exchange modules 2, 21, 22 into a hexagonal cluster, with the outwardly directed end face of each heat exchange module 2, 21, 22 being designed as heat exchangers 3, or the heat exchangers 3 in these are integrated to the outside surfaces. In the operating state we then the Transportfluidum 6, so for example, the air 6 via the outwardly directed surfaces including the heat exchanger 3 sucked by the fans 9, which are provided in the outwardly directed surfaces perpendicular to the boundary surfaces of the heat exchange modules 2, 21, 22 ,

This special design as a heat exchange cluster 1 can always be used particularly advantageous if highest

Heat transfer services are required in the smallest space.

FIG. 13 shows a second exemplary embodiment according to FIG. 12. The embodiment of Fig. 13 differs from that in Fig. 12 essentially in that the placement of the fan 9 and the placement of the heat exchanger 3 is just reversed. That is, the fans 9 are arranged in the example of FIG. 13 in the outwardly facing surfaces, while the heat exchanger 3 in the vertical surfaces in which the angle of inclination α is located and perpendicular to the surface normal in the direction R, or the heat exchanger 3 form these surfaces.

Finally, FIG. 14 shows another embodiment of a heat exchange cluster 1 according to FIG. 12 in a view from the direction R according to FIG. 12. The embodiment according to FIG. 14 differs from that of FIG. 12 in that not six identical heat exchange modules 2, 21, 22 were used with an inclination angle α of 60 °, but only five identical heat exchange modules 2, 21, 22 with an inclination angle α of 72 ° were used. Depending on the requirement, in principle any heat exchange cluster 1 with a number of n identical heat exchange modules 2, 21, 22 can be constructed, each heat exchange module 2, 21, 22 then having an inclination angle α of 3607n.

It is understood that the embodiments described in the context of this application are to be understood as exemplary only. That is, the invention is not limited solely to the specific embodiments described. In particular, all suitable combinations of the specific embodiments presented are also covered by the invention.

Claims

claims

1. Modular heat exchange system comprising a heat exchange module (2, 21, 22) comprising at least a first heat exchange module (21) with a heat exchanger (3), wherein an outer boundary of the heat exchange module (2) by an inflow (4) and a

Outflow surface (5) is formed such that for the exchange of heat between a Transportfluidum (6) and a heat exchanger (3) in the operating state flowing through the heating means (7), the Transportfluidum (6) via the inflow surface (4) the heat exchange module (2) be fed, with the heat exchanger (3) can be brought into flowing contact and via the outflow surface (5) from the heat exchange module (2) again, characterized in that a first boundary surface (81) of the first heat exchange module (2, 21) with respect a second boundary surface (82) of the first heat exchange module (2, 21) is inclined at a predeterminable angle of inclination (α).

2. A heat exchange system according to claim 1, wherein the first boundary surface (81) of the first heat exchange module (2, 21) with respect to the second boundary surface (82) of the first heat exchange module (2, 21) below the predetermined inclination angle

(α) is inclined that the modular heat exchange system by a second heat exchange module (22), in particular in a compact design expandable, wherein the second heat exchange module (22) is preferably identical to the first heat exchange module (21).

3. Heat exchange system according to one of claims 1 or 2, wherein the heat exchanger (3) has a supporting function in the formation of the heat exchange module (2, 21, 22).

4. Heat exchange system according to one of the preceding claims, wherein the heat exchange system of a plurality of heat exchange modules (2, 21, 22) is formed.

5. Heat exchange system according to one of the preceding claims, wherein the inclination angle (α) between the first boundary surface (81) and the second boundary surface (82) of the heat exchange module (2, 21, 22) between 0 ° and 180 °, in particular between 20 ° and 70 °, preferably between 40 ° and 50 °, and more preferably 45 ° and / or the inclination angle (α) is between 90 ° and 180 °, in particular at 120 °.

6. Heat exchange system according to one of the preceding claims, wherein for forming a heat exchange cluster (1) the inclination angle (α) between the first boundary surface (81) and the second boundary surface (82) of the heat exchange module (2, 21, 22) has a value of 3607n and the heat exchange cluster (1) is preferably formed from a number of n identical heat exchange modules (2, 21, 22), wherein preferably to form a hexagonal heat exchange cluster (1) the angle of inclination (α) between the first boundary surface ( 81) and the second boundary surface (2) of the heat exchange module (2, 21, 22) is 60 ° and the hexagonal heat exchange cluster (1) is preferably formed of six identical heat exchange modules (2, 21, 22).

7. A heat exchange system according to any one of the preceding claims, wherein a boundary surface (83) of the heat exchange system is formed by a wall (800) of an installation object, in particular by a wall (800) of a building.

8. Heat exchange system according to one of the preceding claims, wherein to increase a heat transfer rate between the

Heat means (7) and the Transportfluidum (6) a cooling device (9) for cooling the heat exchanger (3), in particular a fan (9) for generating a gas stream (61) is provided, and / or wherein the heat exchange system as a hybrid system (1) is formed, and a sprinkler for sprinkling of the heat exchanger (3) with a cooling fluid, in particular with cooling water, and / or a mist eliminator for the deposition of the cooling fluid is provided.

9. Heat exchange system according to one of the preceding claims, wherein the heat exchanger (3) by a plurality of microchannels (10) is designed as a microchannel heat exchanger (3) and / or wherein the heat exchanger (3) is designed as a laminated heat exchanger (3) with cooling fins and / or the heat exchange system as a

Combined heat exchange system (1) from the laminated heat exchanger (3) and the micro-channel heat exchanger (3) is formed.

10. Heat exchange system according to one of the preceding claims, wherein a foreclosure, in particular a Luftabschottung (11) for regulating a flow rate of the transport fluid (6) is provided.

11. Heat exchange system according to one of the preceding claims, wherein a compensation means for compensating for thermo-mechanical stresses and / or wherein a universal connection element (13) is provided for connecting a component of the heat exchange system.

12. Heat exchange system according to one of the preceding claims, wherein a cleaning system (12, 121, 122) is provided, comprising in particular a dust trap (121) and / or a scraper (121) and / or a dishwasher (121), in particular a cleaning opening (121) and / or a cleaning flap (121) and / or wherein the heat exchanger (3) is provided on the cleaning flap (121) and / or the heat exchanger (3) is designed as a cleaning flap (121).

13. Heat exchange system according to one of the preceding claims, wherein for controlling and / or regulating the heat exchange system in the operating state, a drive unit, in particular a drive unit with a data processing system for controlling the cooling device (9) and / or the cleaning system and / or Luftabschottung (11) and / or an operating or state parameter of the heating means (7) and / or another operating parameter of the

Heat exchange system is provided.

14. Heat exchange system according to one of the preceding claims, wherein the heat exchange module (2, 21, 22) and / or the heat exchanger (3) and / or, a boundary surface of the heat exchange module (2, 21, 22), in particular the entire heat exchange system (2 , 21, 22), made of a metal and / or a

Metal alloy is made, in particular from a single metal or a single metal alloy, in particular made of stainless steel, in particular made of aluminum or an aluminum alloy, wherein preferably a sacrificial metal is provided as corrosion protection, and / or wherein the heat exchange system (2, 21, 22) at least partially provided with a protective layer, in particular with a corrosion protection layer.

15. Heat exchange system according to one of the preceding claims, wherein the heat exchange system is a radiator, in particular a radiator for a vehicle, in particular for a land vehicle, for a

Aircraft or for a watercraft, or a cooler, a condenser or an evaporator for a mobile or stationary heating system, cooling system or air conditioning is, in particular a cooler device for a machine, a data processing system or for a building.