EP2307841A1

EP2307841A1 - Heat exchanger block, and a method for wetting a heat exchanger block

Info

Publication number: EP2307841A1
Application number: EP08760738A
Authority: EP
Inventors: Gert Dierks
Original assignee: A-Heat Allied Heat Exchange Technology AG Germany
Current assignee: A-Heat Allied Heat Exchange Technology AG Germany
Priority date: 2008-06-09
Filing date: 2008-06-09
Publication date: 2011-04-13
Also published as: WO2009149745A1; US20110079371A1; AU2008357596A1; JP2011523016A

Abstract

The invention relates to a heat exchanger block (1) comprising a heat exchanger (4, 41, 42) which is arranged between an inflow surface (2) and an outflow surface (3) such that, for the exchange of heat between a transport fluid (5) and a heat medium (6) which flows through the heat exchanger (4, 41, 42) in the operating state, the transport fluid (5) can be supplied via the inflow surface (2) to a heat-exchange surface (7) of the heat exchanger (4, 41, 42), can be placed in flowing contact with the heat-exchange surface (7) and can be discharged from the heat exchanger (4, 41, 42) again via the outflow surface. According to the invention, a perforated coolant lance (8) is provided such that a coolant (9) can be introduced via the coolant lance (8) between two heat-exchange surfaces (7) of the heat exchanger (4, 41, 42). The invention also relates to a method for wetting a heat exchanger block (1).

Description

Heat exchanger block, and a method for wetting a heat exchanger block

The invention relates to a heat exchanger block and to a method for wetting a heat exchanger block according to the preamble of the independent claims 1 and 13.

The use of heat exchange systems is well known in a nearly intangible number of prior art applications. Heat exchangers are used in refrigerators, e.g. in ordinary

Household refrigerators used 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 countless other applications, all of which are well known to those skilled in the art.

There are different ways to classify heat exchangers from different applications. One try is to make a distinction according to the construction or the production 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 used in the

Heat exchanger system circulates. 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. 1 shows a simple example of such a known laminated heat exchanger 41 '. In practice, an entire Heat exchanger block 1 'often formed by a plurality of such elements according to FIG. In the simplest case, such a laminated heat exchanger 41 'by a plurality of cooling fins 413' is formed, whereby the heat exchange surface T can be massively increased. In the operating state flows through the coolant lines 411 'a heating means 6', so that the heating means 6 'mainly via the cooling fins 413' with the environment, usually with the ambient air 5 'can exchange heat by the ambient air 5' as Transportfluidum 5 'for transport the heat, for example, by means of a fan in the direction of the arrow 5 'according to FIG. 1 by the heat exchanger 41' is transported.

It should be noted at this point that features of known devices from the prior art are provided with an apostrophe in the context of this application, while features of inventive embodiments do not carry an apostrophe.

The ratio of the outer surface to the inner surface depends on the lamella geometry (= pipe diameter, pipe arrangement and pipe spacing), as well as on the lamellar spacing d '. 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 2 mm, which is a typical value for condenser and recooler.

The production of these so-called laminated heat exchangers 41 'is carried out according to a long-known standardized process: The cooling fins 413' are punched with a press and a special tool and punched out according to a predetermined scheme and the punch-outs 412 'provided for spacing with collar 414'. Then, the cooling fins 413 'are put into packages to each other. Subsequently, the pipes that will later transport the heating means 6 ', that is the Coolant lines 411 'in the collar 414' and thus inserted through the punched 412 'and either mechanically or hydraulically expanded so that a very good contact and thus a good heat transfer between the coolant line 411' and cooling plate 413 'is formed. The individual coolant lines 411 'are then indicated by arcs and

Collecting and distribution pipe interconnected, often soldered together. For reasons of clarity, the collection and distribution pipes in Fig. 1 are not shown.

To illustrate the construction of the heat exchanger 41 'according to FIG. 1, a detail of a plan view from direction R to the heat exchanger is shown schematically in FIG. 2. Particularly important are the collar 414 ', through which the coolant lines 411' are guided, since this ensures that the cooling fins 413 'comply with a defined distance d'.

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 all the more effective, the higher the conductivity or the thickness of the lamella, but also the smaller the distance between the tubes. 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 cost could be reduced by reducing the pipe diameter and wall thickness, ie building a heat exchanger with many small pipes rather than a few large pipes. Thermodynamically, this solution would be optimal: very many tubes in close distance 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 according to 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 microchannel heat exchanger employs extruded aluminum sections which have very many small channels with a diameter of e.g. about 1 mm. Such, also known per se MicroChannel heat exchanger block 1 'is shown schematically in Fig. 3. The MicroChannel heat exchanger block 1 'of Fig. 3 is formed by two known per se heat exchanger 42' in the form of extruded profiles 42 '. The two extruded profiles 42 'of FIG. 3 are preferably in thermal contact with a corrugated cooling fin 413', so that the heat medium 6 'carried by the microchannels 421' will be heat with the transport fluid 5 ', preferably air 5'. which, for example, with a fan, not shown in the direction of the arrows 5 'is transported through the heat exchanger block 1', can exchange better.

In practice, a heat exchanger block 1 ', depending on the required heat output, already manage with a single extruded profile 42' as a central heat exchange element. Of course, in order to achieve higher heat transfer rates, a plurality of extruded profiles 42 'can also be provided simultaneously in a single heat exchanger block 1', which are connected to each other in suitable combinations, for example via and to each other, for example with each other are soldered, which is not shown for reasons of clarity in Fig. 3.

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

These profiles can not, and you do not need to widen and they are not inserted into stamped plate packs.

Instead, for example, between two closely spaced profiles (common distances, for example, <1cm) explained as in Fig. 3 sheet metal strips, in particular aluminum sheet laid, 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).

Microchannel heat exchangers have become established in mobile use during the 90s. The low weight, the low block depth and the limited dimensions required here are the ideal ones

Requirements for this. Car radiator and condenser and evaporator for Automobile 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 volumes in the automotive sector, the production processes for mini-channel heat exchangers have standardized and improved, so that one can call this technology today 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 compared with aluminum, is now causing this technology to become increasingly interesting for stationary use as well.

It has long been known that by evaporating water on air-cooled heat exchanger surfaces two to three times more heat can be dissipated than by convection, and this at a lower temperature level, because in evaporation the decisive air temperature is the wet bulb temperature. This fact is exploited, among others, but not only in dry coolers. The wetting of the heat exchanger surface takes place in the prior art by spraying by means of nozzles in front of the heat exchanger block on the air intake side.

Incidentally, the previously described wetting methods should not be confused with the so-called adiabatic cooling. Here, water is so misted in front of the heat exchanger surface on the suction side, that the fine drops of water are absorbed by the air, and due to the evaporation of the drops, the temperature of the sucked air lowers to near the wet bulb temperature.

This method has numerous problems in practice and is in little demand by the customer for a variety of reasons.

On the one hand, in such hybrid coolers, the cooling water can not be effectively transferred to the entire heat exchange surface of the heat exchanger. On the other hand, targeted application of cooling water is indicated in many applications. For example, in a condenser in which the upper part is used as a heater to take into account that this upper part must not be wetted because of the high temperatures occurring.

However, this can not be prevented if, as described above, in the known methods, the wetting of the heat exchanger surface by spraying by means of nozzles takes place in front of the heat exchanger block on the air intake side.

Another problem arises from the fact that the added cooling water is also used to clean the heat exchanger. For this purpose, however, it has hitherto been necessary to work with eight to ten times the excess water in order to prevent soiling of the heat exchanger wash out. This causes the heat exchanger much more Kühlbzw. Cleaning water must be supplied, as is ultimately evaporated during the actual cooling process. Therefore, the excess cooling water must be collected in drip pans and processed consuming. In addition, it is feared that the drip trays aerosols with pathogens get into the air and be distributed.

The object of the invention is therefore to provide an improved heat exchanger block, in particular hybrid heat exchanger, which overcomes the problems known from the prior art. This means, in particular, it should be made available by the invention, a heat exchanger block with which very effective and resource-saving heat from a heat exchanger to a Transportfluidum, preferably, but not only on air transferable, and at the same time very effective and environmentally friendly cleaned and can be operated.

Moreover, it is an object of the invention to provide a particularly effective method for wetting a heat exchanger block.

The objects of the invention solving these objects are characterized by the features of independent claims 1 and 13.

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

The invention thus relates to a heat exchanger block comprising a heat exchanger arranged between an inflow surface and an outflow surface, such that heat exchange between a transport fluid and a heat medium flowing through the heat exchanger in the operating state, the transport fluid can be fed via the inflow surface of a heat exchange surface of the heat exchanger, with the heat exchange surface can be brought into flowing contact, and over the Outflow of the heat exchanger is wegführbar again. According to the invention, a perforated coolant lance is provided, so that a coolant can be introduced via the coolant lance between two heat exchange surfaces of the heat exchanger.

It is thus an essential realization of the invention that the

Heat exchange between heat exchanger and transport fluid, e.g. between the heat exchanger and air, which is passed through the heat exchanger, can be significantly improved by a coolant, which is preferably but not necessarily water, via a coolant lance directly into the interior of the heat exchanger on the

Heat exchanging surfaces is spent in the heat exchanger.

For this purpose, according to the invention, a perforated tube or a perforated or porous tube is provided on the heat exchanger block, with which the coolant between two heat exchange surfaces of the heat exchanger can be introduced.

This means that through the coolant lance, the heat exchange surfaces of the heat exchanger can be wetted in a targeted and controlled manner with coolant. Depending on how the refrigerant lances are placed in the heat exchanger, thus, for example, over the entire heat exchanger, a very uniform cooling performance can be adjusted. In another case, e.g. in a condenser, it may be useful to provide the heat exchanger block only partially with refrigerant lances, so that, for example, operated as a heater, usually upper part of the heat exchanger is not additionally cooled with the liquid coolant, while the remaining, lower part on the refrigerant lances is supplied with coolant.

Of course, a non-uniform distribution of the cooling capacity in the heat exchanger block can also be achieved by other measures become. It is thus possible, for example, for different coolant lances to be used in different regions of the heat exchanger block, which supply different amounts of coolant to the different regions. For example, the different coolant lances may have different perforations, eg have different large perforations or holes through which the coolant is introduced between the two heat exchange surfaces.

It is also possible to use different thick coolant lances, so that the flow rate of coolant in different areas of the heat exchanger is different.

Also, as a function of time, the cooling capacity in a heat exchanger block according to the invention can be controlled and / or regulated simply and efficiently, for example by controlling the working pressure of the coolant as a function of time and / or as a function of location in all or in certain coolant lances / or regulated.

At the same time, a targeted and very efficient cleaning of the heat exchanger block according to the invention is possible by using the coolant lances. Since the coolant is brought into the heat exchanger in the place where it is needed immediately, it can be very easily and efficiently dosed, and it does not need to be worked in particular with multiple excess water. In many cases, therefore, eliminates a drip pan, since no excess water is obtained in the operating condition. As a result, the formation of polluted aerosols is substantially prevented and valuable coolant saved. Even the time-consuming cleaning of excess cooling water is eliminated.

It is even possible that in systems where, in principle, no additional coolant is needed, still refrigerant lances according to the present Provide invention, which then serve only to clean the heat exchanger block.

Either for cleaning during operation, by working only with a very small, irrelevant for cooling amount of coolant. Or, for example, by using the refrigerant lances to clean the heat exchanger block during breaks in operation.

Specifically, the wetting method proposed by the present invention is thus that, for example, in a laminated heat exchanger, replacing a first row of tubes in the direction of air by refrigerant lances in the form of tubes or porous tubes provided with small holes or nozzles making up the Wetting water, so the coolant exits and is introduced into the disk pack. So that the wetting water can be distributed well on the surfaces of the lamellae, the perforation of the first row of tubes of the lamellae or collar, that is executed without spacers. The pipes or hoses used as coolant lances are preferably not expanded or otherwise fixed, but are loosely inserted.

A row of tubes, in particular a first row of tubes of the plate pack of the air-cooled heat exchanger can be provided for example partially or completely with coolant lances. Partial assembly is, as already mentioned, particularly useful if the heat exchanger is used as a condenser and the upper part of the same as a heater, which must not be wetted with coolant because of the high temperatures. The regulation of the amount of coolant can be done, if necessary, for example, via the working pressure of the coolant. It is understood that, instead of just equipping the first row of pipes with coolant lances, the coolant lances can also be placed in any meaningful arrangement in the disk pack and can be provided with appropriate perforations.

Instead of removing coolant lines in the disk pack and replacing them with coolant lances, which automatically leads to a loss of heat exchange capacity, it is also possible to provide separate bores, preferably without collars and in particular smaller diameter, on the laminations in a predetermined arrangement.

Instead of the coolant lances in the form of wetting tubes with holes or nozzles, so-called filter hoses can also be used, sometimes called sweating hoses, which clean the coolant, ie for example the wetting water, wherein the degree of purity of the filtered coolant depends on the quality of the filter hose. The hoses can also be cleaned by rinsing off the filtrate.

Depending on the application, special coolant or wetting liquids are used instead of ordinary water, e.g. demineralized or distilled water or otherwise specially modified water or, in very special cases, other refrigerants known to those skilled in the art.

Of course, according to the present invention, the same principle can also be used for the wetting and cooling of microchannel heat exchangers of the type described above. The peculiarity here is that here preferred, but not necessary flat tubes are used for wetting, the loose between the protruding lamellae after soldering the

Microchannel heat exchanger can be inserted. Would the refrigerant lances configured as flat tubes work together with the MPE tubes soldered, there would be the danger that the holes of the slits of the flat tube would close with solder and thus would no longer be available for the wetting with coolant.

It is understood that even in a heat exchanger block, which is formed from Microchannelwärmetauschern, more or less round tubes or hoses can be used as coolant lances and vice versa that flat tubes can be used advantageously as a coolant lances in special cases in laminated heat exchangers.

Thus, in a particularly preferred embodiment of a heat exchanger block according to the invention, the heat exchanger is designed as a laminated heat exchanger, wherein a coolant line is provided in a punched-out cooling plate.

In an embodiment which is important for practice, the coolant lance is provided in a separate bore in the cooling lamella, so that the number of coolant lines is not reduced by the introduction of the coolant lance. It is of course also possible that a coolant line is removed and the coolant lance is provided in the punched-out of the cooling fins.

It is understood that in one and the same heat exchanger partly coolant lines can be replaced by coolant lances and at the same time additional separate holes can be provided for more refrigerant lances.

In a further important exemplary embodiment of a heat exchanger block according to the invention, the heat exchanger is formed by a multiplicity of microchannels as a microchannel heat exchanger. In that case, the coolant lance is preferably a tube perforated in the form of holes and / or slots, and is provided in particular in the form of a flat tube. As already mentioned, in particular when the coolant has to have a certain purity, a filter hose may be provided as the coolant lance, so that the coolant is automatically cleaned of certain impurities before it is applied to the heat exchange surface.

For very specific applications, a heat exchanger block according to the invention may be formed as a combination block of the laminated heat exchanger and the microchannel heat exchanger. This may be the case, for example, if different conditions prevail at different locations with one and the same heat exchanger block and / or different heat outputs must be provided.

In a manner known per se, of course, in order to increase a heat transfer rate between the heating medium and the transport fluid, a cooling device for cooling the heat exchanger, in particular a fan for generating or amplifying a gas flow of the transport fluid, may additionally be provided.

For controlling and / or regulating the heat exchanger block, advantageously a known control unit, in particular a control unit with a data processing system for controlling a cooling machine and / or a cooling device and / or the supply of the coolant via the coolant lance and / or an operating or state parameter the heating means and / or another operating parameter of the heat exchanger block may be provided.

Preferably, the heat exchanger and / or the entire heat exchanger block, made of a metal and / or a metal alloy, in particular of a single metal or a single metal alloy, in particular stainless steel, in particular aluminum or made of a metal alloy, and / or made of a metal combination, for example of aluminum and copper, wherein a sacrificial metal is preferably provided as corrosion protection, and / or wherein the heat exchanger block is at least partially provided with a protective layer, in particular with a corrosion protection layer.

A heat exchanger block according to the invention may e.g. is a cooler, 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.

The invention further relates to a method for wetting a heat exchanger block comprising a heat exchanger arranged between an inflow surface and an outflow surface so that the transport fluid is supplied via the inflow surface to a heat exchange surface of the heat exchanger for exchanging heat between a transport fluid and a heat medium flowing through the heat exchanger Heat exchange surface is brought into flowing contact, and is led away over the discharge surface of the heat exchanger again. According to the invention, a perforated coolant lance is provided on the heat exchanger block, and a coolant is introduced via the coolant lance between two heat exchange surfaces of the heat exchanger.

In a preferred embodiment, the heat exchanger is a laminated heat exchanger and / or a microchannel heat exchanger, and a regulation of a wetting amount of the coolant is made, and is preferably carried out by adjusting a working pressure of the coolant. In particular, the wetting of the heat exchanger with coolant for cleaning and / or increasing the cooling capacity of the heat exchanger is made.

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

Fig. 1 is a known from the prior art laminated

Heat exchanger;

FIG. 2 shows the heat exchanger according to FIG. 1 in section; FIG.

Fig. 3 is a known from the prior art

Microchannel heat exchanger;

4 shows a heat exchanger block according to the invention with a laminated heat exchanger;

FIG. 5 shows the heat exchanger according to FIG. 4 in section; FIG.

6 shows a heat exchanger block according to the invention with a

Microchannel heat exchanger;

7 shows a coolant lance in the form of a flat tube.

FIGS. 1 to 3, which show two heat exchangers known from the prior art, have already been discussed in detail at the beginning and therefore need not be considered separately in the following. As a reminder, it should again be pointed out that the features of exemplary embodiments according to the invention are provided with reference symbols which do not carry an apostrophe, whereas the reference symbols in FIGS. 1 to 3, which show known heat exchangers, are provided with apostrophes.

In Fig. 4 is a perspective view of an inventive

Heat exchanger block with a laminated heat exchanger shown schematically.

For reasons of clarity, only one laminated heat exchanger 4, 41 is represented by the heat exchanger block according to the invention according to FIG. 4, which is designated overall by the reference numeral 1 below. It is understood that in practice, the heat exchanger block 1 usually in a conventional manner has other components, such as fans, other heat exchangers 4, 41, manifolds, as well as supply and discharge lines for a heating means 6, the heat exchanger 4, 41 for the exchange of heat flows through, etc ..

The inventive heat exchanger block 1 according to FIG. 4 comprises a heat exchanger 4, 41 arranged between an inflow surface 2 and an outflow surface 3, so that the transport fluid 5 is exchanged for heat between a transport fluid 5 and a heat medium 6 flowing through the heat exchanger 4, 41 during operation about the

Inlet surface 2 of a heat exchange surface 7 of the heat exchanger 4, 41 can be fed, can be brought into flowing contact with the heat exchange surface 7, and on the outflow surface 3 from the heat exchanger 4, 41 is again wegführbar. According to the present invention, the heat exchanger block 1 comprises a perforated coolant lance 8, so that a coolant 9 can be introduced via the coolant lance 8 between two heat exchange surfaces 7 of the heat exchanger 4, 41. In the specific embodiment of FIG. 4, the heat exchanger 4 is formed as a laminated heat exchanger 41. In a manner known per se, as already described in detail in the discussion of the prior art, coolant lines 411 are provided in cutouts 412 of the cooling fins 413.

The laminated heat exchanger 41 is thus formed by a plurality of cooling fins 413, whereby the heat exchange surface 7 is massively increased. In the operating state flows through the coolant lines 411 a heating means 6, so that the heating means 6 mainly via the cooling fins 413 with the environment, usually with the ambient air 5 can exchange heat by the ambient air 5 as Transportfluidum 5 for transporting the heat, for example by means of a In Fig. 4 fan not shown in the direction of the arrow 5 is transported through the heat exchanger 41.

In the example of FIG. 4 selected coolant lines 411 have been removed from their punched-412 according to a predetermined scheme, or even in the manufacture of the heat exchanger 41 not even in the associated punched 412 has been used. Instead, cooling lances 8 have been provided in these punched-out portions 412 of the cooling fins 413, through which coolant 9, in practice often water 9, but preferably not necessarily demineralized water 9, can be introduced between two heat exchange surfaces 7 of the laminated heat exchanger 41. The collar 414, with which a predeterminable distance between the cooling fins 413 is adjustable and through which the coolant lines are guided, have also been removed from the expansions 412, through which the coolant lances are guided, or not at all during the production of the heat exchanger 41 been used. Because the collars 414 on the coolant lances 8 are dispensed with, an optimal distribution of the coolant on the heat exchange surfaces 7 is guaranteed. It goes without saying that the coolant lances 8 can also be provided in a separate bore in addition to the existing coolant lines 411 in the cooling lamella 413. This has the great advantage that the heat exchange performance of the heat exchanger 41 is practically not reduced by the presence of the coolant lances 8, since the number of

Coolant lines 411 by the presence of the coolant lances 8 in the package of the cooling fins 413 remains unchanged.

In order to clarify the construction of the heat exchanger 41 according to FIG. 4, a detail of a plan view from the direction R, as defined in FIG. 4, is shown schematically on the heat exchanger 41 in FIG. It is important to note that the collars 414 are missing from the bushings 412, through which the coolant lances 8 pass through the cooling fins 413, while the collars 414 are also missing in the heat exchanger block according to the invention at the bushings 412, through which the coolant lines 411 are guided 1 are still present, thereby ensuring that the cooling fins 413 comply with a defined distance d.

It can be seen very clearly from FIG. 5 how, by using the coolant lances 8, the coolant 9 can be optimally introduced and distributed between two heat exchange surfaces 7 of the heat exchanger 41.

6, another very important embodiment of a heat exchanger block 1 according to the invention is shown partially and in perspective view schematically. The heat exchanger 4 according to FIG. 6 is characterized by a multiplicity of microchannels 421 as microchannel heat exchanger 42, as mentioned as well

Microchannel heat exchanger 42 referred formed. Instead of small tubes, as explained above, the microchannel heat exchanger 42 uses extruded aluminum sections which have very many small channels with a diameter of, for example, about 1 mm. The heat exchanger block 1 of FIG. 6 is in principle such a per se known MicroChannel heat exchanger block 1, wherein the inventive heat exchanger block 1 shown in Fig. 6 by the known heat exchanger blocks V, as shown for example in Fig. 3, differs in that here there is a perforated coolant lance 8 in the form of a flat tube 8, whereas in the prior art it was previously unknown.

The MicroChannel heat exchanger block 1 of FIG. 6 is formed in a manner known per se by two or more known heat exchangers 42 in the form of extruded profiles 42. Opposite extruded profiles 42 of FIG. 6 are preferably in thermal contact with a corrugated cooling fin 413 so that the heat medium 6 carried by the microchannels 421 will be heat with the transport fluid 5, preferably air 5, for example, with a non-illustrated Fan is transported in the direction of the arrows 5 through the heat exchanger block 1, can exchange better.

In practice, a heat exchanger block 1, depending on the required heat output, can already manage with only one pair of extruded profiles 42 as a central heat exchange element. In order to achieve higher heat transfer rates, it is of course also possible to provide a plurality of extruded profiles 42 simultaneously in a single heat exchanger block 1, which are connected to each other in suitable combinations, for example via inlets and outlets, for example soldered together, which is not shown in FIG. 6 for reasons of clarity is. In the heat exchanger block 1 of FIG. 6 is provided as a coolant lance 8 in the form of holes 81 and / or slots 81 perforated flat tube 8, which is inserted as shown between two extruded profiles, so that coolant from the flat tube 8 on the heat exchange surfaces 7, the wavy are arranged between two opposite extruded profiles 42, can be applied.

For clarification, such a perforated flat tube 8 is again shown separately in FIG. Since flat tube is at the side facing the heat exchange surfaces of the heat exchange block 1 in the installed state, with a plurality of perforations, so holes or

Slots provided so that the coolant 9 can be optimally applied to the heat exchange surfaces in the operating state.

It is understood that in certain cases instead of perforated flat tubes 8 and perforated round tubes 8, perforated tubes 8 or filter tubes 8, especially Schwitzschläuche 8, or any other coolant lance 8 advantageous in a heat exchanger block 1 according to the invention, even if the heat exchanger block 1 from Microchannelwärmetauschern 42 is constructed, can be used.

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 . A heat exchanger block comprising a heat exchanger (4, 41, 42) arranged between an inflow surface (2) and an outflow surface (3) so as to exchange heat between a transport fluid (5) and the heat exchanger (4, 41, 42) in the operating state flowing through the heat medium (6), the Transportfluidum (5) via the inflow surface (2) of a heat exchange surface (7) of the heat exchanger (4, 41, 42) can be fed, with the heat exchange surface (7) can be brought into flowing contact, and the outflow surface (3) from the heat exchanger (4, 41, 42) is again wegführbar, characterized in that the

Heat exchanger block comprises a perforated coolant lance (8), so that a coolant (9) via the coolant lance (8) between two heat exchange surfaces (7) of the heat exchanger (4, 41, 42) can be introduced.

2. Heat exchanger block according to claim 1, wherein the heat exchanger (4) as a laminated heat exchanger (41) is formed, wherein a coolant line (41 1) in a punched-out (412) of a cooling fin (413) is provided.

3. Heat exchanger block according to claim 2, wherein the coolant lance (8) is provided in a separate bore in the cooling fin (413).

4. heat exchanger block according to claim 2 or 3, wherein a coolant line (41 1) is removed and the coolant lance (8) in the punched-out (412) of the cooling fins (413) is provided.

5. Heat exchanger block according to claim 1, wherein the heat exchanger (4) through a plurality of microchannels (421) as a microchannel heat exchanger

(42) is formed.

6. heat exchanger block according to claim 5, wherein as the coolant lance (8) in the form of holes (81) and / or slots (81) perforated tube (8), in particular flat tube (8) is provided.

7. heat exchanger block according to one of the preceding claims, wherein a filter tube is provided as a coolant lance (8).

8. Heat exchanger block according to one of the preceding claims, wherein the heat exchanger block is formed as a combination block of the laminated heat exchanger (41) and the microchannel heat exchanger (42).

9. Heat exchanger block according to one of the preceding claims, wherein to increase a heat transfer rate between the heating means

(6) and the transport fluid (5) a cooling device for cooling the heat exchanger (4, 41, 42), in particular a fan for generating a gas flow is provided.

10. Heat exchanger block according to one of the preceding claims, wherein for controlling and / or regulating the heat exchanger block, a

Control unit, in particular a control unit with a data processing system for controlling a cooling machine and / or a cooling device and / or the supply of the coolant (9) via the coolant lance (8) and / or an operating or state parameter of the heating means (6) and / or a other

Operating parameters of the heat exchanger block is provided.

1 1. Heat exchanger block according to one of the preceding claims, wherein the heat exchanger (4, 41, 42) and / or the entire heat exchanger block is made of a metal and / or a metal alloy, in particular of a single metal or a single

Metal alloy, in particular made of stainless steel, in particular made of aluminum or an aluminum alloy, and / or from a Metal combination, for example made of aluminum and copper is preferably provided as a corrosion protection sacrificial metal, and / or wherein the heat exchanger block is at least partially provided with a protective layer, in particular with a corrosion protection layer.

12. Heat exchanger block according to one of the preceding claims, wherein the heat exchanger block is a cooler, 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.

13. A method for wetting a heat exchanger block (1) comprising a heat exchanger (4, 41, 42) arranged between an inflow surface (2) and an outflow surface (3), such that for exchanging heat between a transport fluid (5) and the heat exchanger (4, 41, 42) flowing through the heating means (6)

Transport fluid (5) via the inflow surface (2) of a heat exchange surface (7) of the heat exchanger (4, 41, 42) is supplied with the heat exchange surface (7) is brought into flowing contact, and via the outflow surface (3) from the heat exchanger (4 , 41, 42) is led away again, characterized in that on

Heat exchanger block (1) a perforated coolant lance (8) is provided, and a coolant (9) via the coolant lance (8) between two heat exchange surfaces (7) of the heat exchanger (4, 41, 42) is introduced.

14. The method of claim 13, wherein the heat exchanger (4) is a laminated heat exchanger (41) and / or a microchannel heat exchanger (42), and a regulation of a wetting amount of the coolant (9). is made, preferably by adjusting a working pressure of the coolant (9) is made.

15. The method according to claim 13 or 14, wherein the wetting of the

Heat exchanger (4, 41, 42) with coolant (9) for cleaning and / or increasing the cooling capacity of the heat exchanger (4, 41, 42) is made.