WO2007009713A1

WO2007009713A1 - Heat exchanger

Info

Publication number: WO2007009713A1
Application number: PCT/EP2006/006997
Authority: WO
Inventors: Peter Geskes Geskes; Ulrich Maucher; Jens Richter; Jens Ruckwied
Original assignee: Behr Gmbh & Co. Kg
Priority date: 2005-07-19
Filing date: 2006-07-17
Publication date: 2007-01-25
Also published as: EP1913324A1; EP1913324B1; JP2009501892A; ATE524700T1; US20080202735A1

Abstract

The invention relates to a heat exchanger (1) with flow channels (3), which can be flowed through from a common first inlet to a common first outlet by a first fluid, comprising a housing (2), which accommodates the flow channels (3) and which can be flowed through by a second fluid from a second inlet area to a second outlet area. The flow channels (3) have a flat cross-section as well as longitudinal sides (3a) and are flow-connected to one another. The invention provides that the longitudinal sides (3a) of the flow channels (3) are integrally connected to the housing (2), particularly by soldering.

Description

Heat exchanger

The invention relates to a heat exchanger according to the preamble of claim 1 - known from DE 100 60 102 A1.

By the US 2003/0010479 A1, a heat exchanger was known, which can be used as an exhaust gas cooler in an EGR system (exhaust gas recirculation system). In a housing, which is flowed through by liquid coolant of the cooling circuit of an internal combustion engine, exhaust pipes are arranged, which are accommodated at the end in tube sheets, which in turn are connected to the housing. The exhaust gas is supplied to the exhaust gas cooler via a diffuser, then flows through the exhaust pipes surrounded by the coolant and exits the cooler via an exhaust gas outlet. All parts of the exhaust gas cooler are soldered together. A disadvantage of this design with tube plates in which the pipe ends are added, is that the tubes are fixed during the soldering process in the tube sheets and thus can not move towards each other during soldering and melting of the solder layer, which u. a. also adversely affects the soldering of the turbulence inserts with the pipe inner walls. This disadvantage is avoided by systems without tube bottoms, as the following example shows:

DE 100 60 102 A1 has disclosed a heat exchanger which can also be used as an exhaust gas cooler in an EGR system. In this case, recirculated exhaust gas is cooled by coolant, which is taken from the cooling circuit of the internal combustion engine of the motor vehicle. The known exhaust gas cooler has a substantially two-part housing, in which a heat-flow on the primary side of the cooling body, consisting of a plurality of flat tubes, is arranged and secondary side of the exhaust gas flows through. In this case, the exhaust gas is relatively straight, ie guided without significant deflections through the housing. The coolant is fed in and out at right angles to the flat tubes, so that 90 degrees of deflections result. To improve the heat transfer between exhaust gas and coolant so-called turbulence plates are arranged between the flat tubes. The entire exhaust gas cooler, consisting of housing, tubes and turbulence plates, is produced by "one-piece soldering".

According to FIG. 9, the subject of the application DE 100 60 102 A1 proceeds from a prior art relating to a housing-free exhaust gas heat exchanger, wherein flat exhaust pipes are formed from disks, the fold of which has raised edge strips angled on the longitudinal sides, which have adjacent edge strips are soldered to a housing wall. The disadvantage here is that there is a large number of solder joints, each of which carries the risk of leakage and thus exhaust leakage. A disadvantage of the subject of the application of DE 100 60 102 A1 is that the housing walls are acted upon directly by the exhaust gas flow and thus heated to a temperature which the environment of the installed exhaust gas cooler, for. B. the engine compartment of a motor vehicle is not conducive.

It is an object of the present invention to make a heat exchanger of the type mentioned on the one hand joint, in particular soldering, welding, adhesive, etc. and on the other hand to keep its outside temperature low when using hot, to be cooled media.

This object is solved by the features of claim 1.

According to the invention, it is provided that the flow channels, which are preferably designed as pairs of disks, are longitudinally connected to the walls of the housing cohesively connected, ie soldered, welded, glued, etc. are. The pairs of discs are stacked in a package and fluidly interconnected by transverse channels. In the flow through these transverse channels, a comparatively high pressure loss, on the one hand by the deflection of the fluid from the transverse channel in the trapped by the disc pairs channels, but in particular by the fact that the transverse channels between the disc pairs usually have sharp edges, leading to a strong turbulence of the fluid and thus lead to high pressure losses. The pairs of discs are therefore traversed by a first fluid, preferably a liquid coolant, for which the pressure losses in the cooler are less crucial. The package of disk pairs is the front side of a second fluid, in particular a hot medium to be cooled, flows and flows through, so that a relatively straight flow through the disk pack, ie without substantial deflections is achieved. This results in a low pressure drop for the second, preferably gaseous, fluid. In adaptation to the heat transfer conditions turbulence generating devices are provided between the discs. The heat exchanger according to the invention is preferably soldered, welded, glued, etc. in a single operation. The parts to be soldered, welded or adhesively bonded are flexible, ie movable relative to one another and can therefore move relative to one another during melting of the solder layers during the soldering process that minimal solder gaps and proper soldering are achieved. Advantageously, the pairs of disks can be prefolded and / or crimped in a joining process, in particular the soldering process, welding process, bonding process, etc., ie the disk pair consisting of two disks, including possibly provided turbulence inserts, can be prefabricated in such a way that the pair of disks passes through from the one disk formed and the edge of the other disc comprehensive tabs is fixed so that the two disc plates of the disc pair no longer slip against each other during the actual soldering process, no longer move against each other or can diverge, and so ensures the tight soldering of the disc pair is. For example, crimped disks can prevent, for example, relative - A -

Movements between the housing and the longitudinally adjacent pair of discs by different rapid heating of the components and the melting solder layers lead to insufficient soldering of the disc pair. This also facilitates the tolerance vote between see the longitudinal side of the disc pair and the housing, since essentially only the system of the crimped pair of discs on the housing during the soldering process must be ensured without having to consider possible shifts of the two discs against each other. This ensures that heat conduction takes place between the first fluid, the cooling medium, and the housing walls as a result of the cohesive connection of the flow channels or disk pairs. Due to the thermal coupling, the housing wall also contributes to the heat transfer, and the connection of the pairs of disks can considerably increase the heat-transferring area for the second fluid depending on the heat exchanger geometry and design of the turbulence generators: from approx. 2% to more than 10% if a turbulence sheet in the channel for the second fluid is provided and even up to> 25% when turbulators (for example, embossed in the disc Verwir- bungskörper) are used in the channel of the second fluid. Thus, an increase in the heat exchanger performance is achieved, which can be significant. Furthermore, the housing wall can be sufficiently cooled when using a hot medium to be cooled and kept at a relatively low temperature level. In particular, in exhaust gas coolers but also in intercoolers in many other heat exchanger applications, a sufficient cooling of the housing is often mandatory because otherwise very high thermoelectric voltages at the junctions between the housing and disc pairs caused by the large temperature differences and correspondingly different thermal expansions of the exhaust gas leading housing and the cooled disc pairs are caused. Another significant advantage of the connection of the longitudinal sides of the disk pairs to the housing is a considerable increase in the compressive strength of the heat exchanger with respect to the second fluid, since the disks represent tie rods between the two sides of the housing, which counteract the internal pressure. Thus, the presented heat exchanger concept is particularly suitable for media in which the pressure loss requirements for the second fluid are very restrictive, the second fluid is very hot, or high pressures of the second fluid are present, or combinations of these requirements.

In one development of the invention, the flow channels are materially connected over the longitudinal sides substantially over their entire length with the housing. In particular, the cohesive connection by soldering, welding, gluing, etc., in principle, any other type of connection such as a positive connection o- a combination of a cohesive and a positive connection is possible.

In one embodiment of the invention, the flow channels are designed as pairs of discs. The pairs of discs form passageways for a second fluid. There is a connection between the disk pairs and the housing, so that the second fluid has access to the housing and to the housing wall and thus, for example, cools or heats the housing wall and the housing.

In one development of the invention, the flow channels and / or the passageways are received substantially in their entirety by the housing, so that the heat transfer between the first and the second fluid substantially completely inside a housing which is closable with a lid occurs , wherein there is also a heat transfer between the second fluid and the housing and / or the lid, as well as between the first fluid and the housing and / or the housing cover.

In one development of the invention, a fluid, in particular the first fluid, is formed between the cover of an adjacent disk, in particular a lower disk, at least one flow channel, in this way a top disk can be saved and the cover is simultaneously cooled as well. Since the lid to the housing by material bond, such as soldering, welding, gluing, etc., and / or by positive engagement, such as forming, a heat transfer between the lid and the housing and vice versa, so that the housing is also cooled. In another embodiment of the invention, at least one flow channel of the first fluid is formed between the bottom portion of the housing or the housing shell and an adjacent disc, in particular the upper disc, and between the bottom portion of the housing shell, in this way also a disc, in particular a lower disc , saved. The first fluid in particular cools the housing and the housing shell. In addition, however, it is also possible to connect the upper disk to a lower disk, in particular by material bonding, whereby a pair of disks is formed, which are materially bonded, in particular by soldering, via at least one disk, in particular with the lower disk adjacent to the bottom area with the housing shell in the bottom area , Welding, gluing, etc. is connected.

In a further development of the invention, the respective lower and upper disk forming a disk pair are connected to one another by a fold formed on the edge, thereby the disks are connected to one another in a form-fitting manner, in particular by bending. In this case, at least one disc, in particular the lower disc, surrounds the other disc, in particular the upper disc, whereby the discs are hooked into one another, wherein tolerance compensation is simultaneously possible in the stacking direction of the discs and the pairs of discs, so that during the joining process, such as soldering, welding, Gluing, etc., with which the cohesive connection is generated, any openings or gaps, can be compensated between the discs, so that the joining process process reliable and successful feasible and so a complete cohesive connection between the discs, especially the upper and the lower disc, but also between adjacent disc pairs and between adjacent upper and lower discs, takes place.

In one development of the invention, an inflow channel and / or at least one outflow channel runs transversely through the pairs of discs, in which case the inflow and / or outflow channel can be at an angle of 0 ° to 360 ° or - 360 ° to the stacking direction of the discs and / or Longitudinal direction of the discs through the pairs of discs, in particular at an angle of - 50 ° to + 50 ° to the stacking direction, particularly advantageous is an angle of 0 ° to the stacking direction, ie outflow and or inflow channel extending substantially parallel to the stacking direction. The angles of the outflow channel and the inflow channel to the stacking direction and / or to the longitudinal direction can be different and assume values between 0 ° and 360 ° or -360 °

In a development of the invention, the pairs of discs have at least one cup or at least one expression. The cup or the stamping is introduced in at least one slice of a pair of discs, preferably by forming such as bending, punching, etc., or by prototyping etc.

In a further development of the invention, the expression or the cup of a disk pair extends to an adjacent disk pair, with the disks and the disk pairs touching each other and, in particular, being bonded together by soldering, welding, gluing etc. In addition, a positive connection and / or a combination of a cohesive and positive connection are possible lent, as well as other compounds.

In a further development of the invention, the expression or cup is introduced into the upper disk, in particular by reshaping or prototyping, as well as an upper disk annular surface which contacts a lower disk ring surface of the lower disk of an adjacent disk pair introduced by primary or Umforms and in particular cohesively by soldering , Welding, gluing, etc. and / or by positive engagement, such as hooking, is connected to the lower disc ring surface.

In another embodiment of the invention another expression, in particular by reshaping and or prototypes in the lower disc is introduced, as well as a lower disc ring surface which touches a Oberscheibenringfläche the upper disc of an adjacent disc pair and in particular cohesively by soldering, welding, gluing, etc. and / or positively connected, as by hooking, with the Oberscheibenringflä- surface.

In a further development of the invention, the flow channels are stacked. Likewise, the passageways can be stacked. In a further development, the disks are stacked such that one disk is stacked on an adjacent other disk and that in particular a top disk is placed on a bottom disk and on the top disk another bottom disk is placed, on which in turn a further top disk is placed, so that adjacent pairs of discs are stacked on top of each other. The stack of disks or the stack of disk pairs is in turn inserted into the housing shell, which is closed with a lid. The cover is placed on the housing such that it is placed in the stacking direction on the housing and with this form-fitting, in particular by soldering, welding, gluing, etc. and / or material fit, in particular by reshaping, hooking, etc., so that During the joining process, in particular soldering, welding or kissing, a tolerance compensation in the stacking direction of the flow channels or the passageways can take place.

In a development of the invention, the disks of a disk pair have disk edge surfaces in such a way that the upper disk of a pair of disks has an upper disk edge surface and the adjacent lower disk has a lower disk rim surface, the upper disk rim surface corresponding to the lower disk rim surface and materially bonded, in particular by soldering, welding, gluing, etc . connected is. The upper disk edge surface extends in the longitudinal direction of the disk substantially parallel to the signing edge surface, just as the upper disk edge surface extends in the direction of the disk width, which is in particular substantially perpendicular to the longitudinal direction of the disk and substantially perpendicular to the stacking direction of the disks and substantially parallel to the lower disk edge surface. In the portions of the upper disc edge surface and the lower disc edge surface, in which the longitudinal side of the disc merges in the stacking direction in the disc width, a collision of the lower and upper disc edge surface is formed such that the Shock of a disc edge surface in the longitudinal direction substantially as a quarter cylinder is formed and that touch the quarter cylinder of the lower and upper disc substantially as two telescoped concentric quarter cylinder and materially, in particular by soldering, welding, gluing, etc. are connected.

In a further development of the invention, the longitudinal sides of two pairs of discs forming a flow channel surround each other at least regionally, in particular over the entire disc length, such that the longitudinal side contacting the housing encompasses the longitudinal side of an adjacent disc, in particular the other disc of the respective disc pair, and that the both disks are crimped together in this way.

In a further development of the invention, the broad sides of two pairs of disks forming a flow channel surround each other at least regionally, in particular over the entire width of the disk. The two disks, in particular the upper disk and the lower disk of a disk pair, are thus crimped together.

In a development of the invention, the disk pairs have turbulence-generating devices, in particular turbulence inserts or impressed structural elements. The turbulence inserts can be designed such that they are punched sheets and / or braided wire mesh. The content of unpublished DE102004037391.4, DE19718064B4 and DE19709601 C2 is hereby expressly disclosed.

In one embodiment of the invention, the characteristics are conical and designed as a truncated cone, which are preferably produced from a disc by forming such as punching or by forming. The smaller diameter of the two diameter having side surface of the truncated cone is formed as an annular surface, which touches the adjacent disc, preferably the lower disc of the next pair of discs and in particular with this cohesively by soldering, welding, gluing, etc. is connected. In one embodiment of the invention, the characteristics are aerodynamic, in particular formed with an elongated or elliptical or round cross-section.

In one development of the invention, turbulence-generating devices are introduced between flow channels or in the passage channels. The contents of unpublished DE102004037391.4, DE19718064B4 and DE19709601 C2 are hereby expressly disclosed in this context.

In a further development of the invention, the rabbet joints are connected to the housing, in particular to the inner surface of the housing, wherein the connection takes place in particular by material bonding by soldering, welding, gluing, etc.

In one development of the invention, the inlet region of the housing in the flow direction of the second fluid is arranged in front of the disk pairs.

In a development of the invention, the outlet region of the housing is arranged in the flow direction of the second fluid behind the disk pairs.

In a development of the invention, the disk pairs of the second fluid can be flowed around substantially parallel to their longitudinal sides.

In one embodiment of the invention, the longitudinal fold is formed by the same direction angled edges of the upper and lower discs. The longitudinal fold also forms a contact surface for the housing.

In one embodiment of the invention, the longitudinal fold is formed by oppositely angled edges of the upper and lower discs. The longitudinal fold also forms a contact surface for the housing.

In a development of the invention, the pairs of disks have side channels in the region of the housing walls for the first fluid. The side channels are formed as an extension of the flow cross section of the disk pairs. The extension has a channel height, which substantially corresponds to the distance between the pairs of discs.

In a further development of the invention, the disk pairs have a flow cross section with a channel width b and the housing walls at a distance w, where b <w and between the flow cross sections and the housing wall material bridges are arranged and which are formed in particular from lower and / or upper disk.

In one embodiment of the invention, the housing is formed at least in two parts, wherein it has a housing shell and a lid.

In one development of the invention, the inlet region of the housing has an inlet connection, which is arranged in the housing shell or in the cover. In addition, the outlet region of the housing has an outlet nozzle, which is arranged in the housing shell or in the lid.

In a development of the invention, the housing has an inlet and outlet connection for the first fluid, wherein the inlet and outlet connections for the first fluid are arranged in the cover or in the housing shell and have longitudinal axes which are inclined relative to the pairs of disks.

In a development of the invention, the heat exchanger has a bypass. Within the housing and parallel to the disc pairs, a bypass passage for the second fluid is arranged. The mass flow of the second fluid is branched off, in particular by a partition wall, into at least two partial mass flows, wherein at least a first partial mass flow of the second fluid flows through the passage channels and at least a second partial mass flow of the second fluid flows through the bypass. In a further development of the invention, the pairs of discs form a package which can be flowed through in two bends by the second fluid. In the inlet region for the second fluid and / or in the outlet region for the second fluid, a partition wall is arranged. In this case, the dividing wall is in particular arranged such that it can rotate such that an angle between the flow direction of the second fluid of a longitudinal side of the dividing wall can be set between 0 ° and 360 °.

In one development of the invention, the heat exchanger includes at least one check valve, which is preferably integrated in the housing and located in the outlet area.

In a further development of the invention, the bypass channel is arranged in the heat exchanger above or below the pairs of discs.

In a development of the invention, the bypass channel is designed as a bypass tube, which can be inserted into the housing. The bypass tube is thermally insulated from the flow channels (3) and / or the passageways, in particular such that the heat transfer between the second partial mass flow, which flows through the bypass channel and / or the bypass tube and the first partial mass flow, which is in particular cooled as possible is low.

In a further development of the invention, the bypass pipe is arranged substantially at a distance from the flow channels and / or the passage channels. The spacing is preferably carried out by means of embossing or punching introduced into the bypass tube and / or into the flow channels and / or the passage channels.

In a development of the invention, the bypass tube consists of at least one partial element, which is preferably designed as an open profile and particularly advantageously as a U-profile or half-tube. In a further development of the invention, the bypass tube comprises two tube halves, which are preferably interconnected by soldering, welding, gluing, etc. cohesively.

In a development of the invention, the bypass tube has at least one longitudinal dividing wall.

In one development of the invention, at least one bypass flap is integrated into the inlet or outlet region of the housing. The bypass damper is adjustable and may assume an angle of 0 ° to 360 °, thereby dividing the mass flow of the second fluid into the first partial mass flow and the second partial mass flow. The first partial mass flow flows through the passage channels and is thereby cooled in particular. The second partial mass flow flows, in particular uncooled through the bypass. By means of the bypass valve, the first partial mass flow of the second fluid through the passageways is adjustable and / or controlled and / or regulated. The second partial mass flow of the second fluid through the bypass results as a function of the set first partial mass flow and is therefore likewise controllable and / or controllable.

In a further development of the heat exchanger, the inlet region has two separate inlet stubs and a partition wall.

In a further development of the invention, the pairs of discs form a package which can be flowed through in two bends by the second fluid. An inlet chamber and an outlet chamber are arranged on the one hand of the disk package. On the other hand, the disk package, a deflection chamber for the second fluid is arranged.

In a development of the invention, the bypass is integrated into the housing. In particular, the bypass is made in one piece with the housing.

In a development of the invention, the bypass is integrated in the cover. In particular, the bypass is made in one piece with the lid. Heat exchanger according to one of the preceding claims, characterized in that the flap is arranged in the inlet region or in the outlet region.

In one development of the invention, the heat exchanger has at least one bypass valve which controls and / or regulates the volume and / or mass flow, in particular of the second fluid, through the bypass. The bypass valve is preferably integrated in the housing and in particular designed in one piece with this. The bypass valve is arranged in the inlet area and / or in the outlet area.

In one embodiment of the invention, the bypass valve is designed as a combination valve, which is referred to below as a heat exchanger valve device. The heat exchanger valve device is characterized in that the valve disc is rotatable between a first open position, in which the bypass outlet is closed and the heat exchanger outlet is open, and a second open position, in which the bypass outlet is opened and the heat exchanger outlet is closed. Due to the rotatable valve disc, a sufficient tightness can be ensured even at high pressures.

A further preferred embodiment of the heat exchanger valve device is characterized in that the rotatable valve disc has a fluid passage opening which can be brought at least partially by twisting at least partially with one of two further fluid passage openings to cover, which are provided in a fixed relative to the valve housing valve disc. The three fluid passage openings are preferably formed congruent to one another.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that one of the fluid passage openings in the fixed valve disc is connected to the heat exchanger outlet and the other fluid passage opening is connected to the bypass outlet. Depending on the overlap of the fluid passage openings in the valve discs passes more or less or even no fluid to the bypass outlet or the heat exchanger outlet.

A further preferred exemplary embodiment of the heat exchanger valve device is characterized in that the fixed valve disk has a depression in which the rotatable valve disk is guided. This provides the advantage that it is possible to dispense with a valve disc guide on the valve housing.

A further preferred embodiment of the heat exchanger valve device is characterized in that the fixed valve disc has an external thread, with which the fixed valve disc is screwed into a complementary formed internal thread of the valve housing. This simplifies the installation of the fixed valve disc.

Another preferred embodiment of the heat exchanger valve device is characterized in that an actuator rod extends from the rotatable valve disk. By the actuator rod, which is preferably guided out of the valve housing, the operation of the rotatable valve disc is simplified.

A further preferred embodiment of the heat exchanger valve device is characterized in that the valve disks are at least partially made of ceramic. Stainless steel can also be used instead of ceramic.

A preferred embodiment of the heat exchanger valve device is characterized in that the valve slide between a first extreme position in which the bypass outlet is closed and the heat exchanger outlet is open, and a second extreme position is movable back and forth, in which the bypass outlet is opened and the heat exchanger outlet is closed. By the valve spool, a sufficient tightness can be ensured even at high pressures. Another preferred embodiment of the heat exchanger valve device is characterized in that the valve slide is partially formed of ceramic. Stainless steel can also be used instead of ceramic.

Another preferred embodiment of the heat exchanger valve device is characterized in that the valve housing is partially formed of ceramic. Preferably, the tread for the valve spool is formed of ceramic.

A further preferred embodiment of the heat exchanger valve device is characterized in that the valve slide is equipped with a sealing element for the input. Preferably, the entrance is equipped with a sealing seat for the sealing element.

A further preferred embodiment of the heat exchanger valve device is characterized in that the sealing element has a sealing surface facing the inlet, which has the shape of a spherical segment. By using a large diameter ball section, it is easier to move the valve spool.

A further preferred embodiment of the heat exchanger valve device is characterized in that the sealing element is guided to the valve slide back and forth movable. As a result, the closure of the inlet with the sealing element, which is also referred to as a closure element, is simplified.

A further preferred embodiment of the heat exchanger valve device is characterized in that the sealing element is biased by a spring device against the input. This allows a tight closure of the input.

Another preferred embodiment of the heat exchanger valve device is characterized in that the valve slide a Pressure equalization channel has. As a result, the displacement of the valve spool in the valve housing is facilitated.

In one development of the invention, the integrated bypass has a pivotable partition, by means of which the inlet connection and the outlet connection are short-circuited.

In one development of the invention, the first fluid is a liquid coolant, in particular the coolant from the cooling circuit of an internal combustion engine of a motor vehicle, and the second fluid is recirculated exhaust gas of the internal combustion engine.

In one development of the invention, the first fluid is air and the second fluid is recirculated exhaust gas of an internal combustion engine of a motor vehicle.

In one development of the invention, the disk package is preceded by an oxidation catalyst, as disclosed in unpublished DE 10 2005 014 295.8. The entire contents of unpublished DE10 2005 014 295.8 are hereby expressly disclosed.

In one development of the invention, the first fluid is a liquid coolant, in particular the coolant of the cooling circuit of an internal combustion engine of a motor vehicle, and the second fluid of the internal combustion engine is deliverable charge air.

In one development of the invention, the first fluid is air and the second fluid of an internal combustion engine of a motor vehicle can be supplied with charge air.

In one development of the invention, the heat exchanger is used as an exhaust gas cooler in an exhaust gas recirculation system of an internal combustion engine of a motor vehicle or as a heater for heating the interior of a motor vehicle, the heat transferred from the second fluid to the first fluid is used to heat the passenger compartment of a motor vehicle To heat the vehicle. In one development of the invention, the heat exchanger is used as an oil cooler for cooling engine oil of an internal combustion engine or transmission oil of a motor vehicle by a liquid coolant, preferably the coolant of the cooling circuit of the internal combustion engine.

In one embodiment of the invention, the heat exchanger is used as a refrigerant condenser in the refrigerant circuit of an air conditioning system for motor vehicles.

In a development of the invention, the heat exchanger is used as a refrigerant exhaust gas cooler in the refrigerant circuit of an air conditioning system for motor vehicles.

In a development of the invention, the heat exchanger is used as a refrigerant evaporator in the refrigerant circuit of an air conditioning system for motor vehicles.

Further advantageous embodiments of the invention will become apparent from the dependent claims.

A particularly advantageous embodiment of the invention are concepts in which the edges of both discs of the pair of discs circumferentially and continuously are formed so that they have everywhere a planar contact with each other (Fig. 1, 2c, 3a, 3b, 3c). This can also be described by the fact that the two disks are formed along their contact line on the circumferential outer edge so that they have an angle of 0 ° to each other in the plane perpendicular to this contact line, this angle is only greater than 10 ° in exceptional cases , In this case, the two disks may, for example, abut surface-to-surface on their contact line, so that, in a section perpendicular to the line of contact, the two disks extend largely parallel to one another over a certain distance. One or both disks may, for example, also be formed spherically against each other in the region of the contact line, so that, in a section perpendicular to the contact line, the contact of a straight line with a circular segment or, if both are crowned, the punctiform contact tion of two circle segments results in only one touch point but no line of contact. Furthermore, both slices may, for example, also be designed at their edges such that one is concave and the other convexly shaped and two circle segments are present in the plane normal to the contact line, which contacts each other only pointwise or over a certain circular arc section. All of these examples have at the circumferential contact line exactly at an angle of 0 ° to each other. The just described embodiment of the pairs of discs can therefore be made very flexible according to the invention because the flow channel for the second fluid is sealed at all sides by the housing and therefore no soldering with adjacent disc edges is required at the outer edges of the pair of discs. Figure 2c represents a good compromise between process-optimized design of the pair of disks, which allows a circumferential flat system with a small contact angle between the two discs, and an excellent thermal connection of the housing to the channel of the first fluid.

According to a further advantageous embodiment of the invention, the housing is formed at least in two parts, ie, for example, from a first trough-shaped housing part, a housing shell, and a second lid-shaped part, a lid formed. Both parts can be put together and simply joined together, in particular soldered, welded, glued, etc. With such a housing concept, an optimal joining process, in particular soldering process, welding process, adhesive process, etc., the stacked pairs of discs is achieved when the housing parts are also inserted in the stacking direction of the disc pairs into each other or superimposed and by soldering, welding, gluing, etc. during the Joining process, in particular the soldering process, welding process, gluing process, etc., are joined to the housing. In a suitable embodiment, then also the housing parts can move to the same extent with the disk pairs aufeinender, so that, for example, by the melting solder layers no gaps or soldering, welding and / or Klebefehlstellen arise. Advantageously, the housing shell as well as the lid can be produced as forming and / or molded parts such as deep-drawn parts, wherein the housing damage Ie can also form the inlet and outlet area for the second fluid. Further, on the housing, be it the housing shell or the housing cover, inlet and outlet nozzles are formed for both the first and for the second fluid, for. B. as passages. The position and shape of the nozzle can be chosen arbitrarily according to the requirements of the heat exchanger. Thus, for the second fluid of the inlet and outlet nozzles at the same end of the radiator or at opposite ends are (see explanations below) and the inlet and outlet can take place in any direction, eg in the longitudinal direction of the radiator, upwards - out here the lid, down from the housing or laterally from the housing.

According to a further advantageous embodiment of the invention, a bypass channel can be arranged in the housing parallel to the disk package, wherein the bypass may be formed, for example, as a tube which is inserted into the housing and soldered to the other parts. Such a bypass is particularly advantageous when using the heat exchanger as the exhaust gas cooler in an exhaust gas recirculation system. Such bypass arrangements in conjunction with corresponding bypass flaps for controlling the exhaust gas flow through the heat exchanger or through the bypass are known per se from the prior art. The construction of the heat exchanger according to the invention allows an integration of a bypass channel and a bypass flap in the exhaust gas cooler with simple means. The bypassed fluid flow must also be conducted separately in the inlet region of the fluid flow, which flows through the heat exchanger channels. For this purpose, a separating plate or separating element, in the simplest embodiment a separating plate, can be provided in the inlet region for the second fluid, which separates the inlet region into two regions, one for the bypass fluid flow and the other for the heat exchanger fluid flow. For example, separating elements can be clamped, welded or soldered into a housing part or between housing parts. The separate inlet regions can either each have their own inlet openings in the housing or can be supplied with the fluid streams by a common inlet opening divided into two parts by the separating element. In the case of the common entry opening, of course, a separation of the the fluid flows in the supply line of the second fluid required, or a bypass valve must be placed directly on the inlet opening in a way that it closes directly with the separator and no impermissible leakage from the bypass to the heat exchanger side and vice versa can occur. This can be done for example by flanging or a flanged module flap, housing and actuator. Furthermore, the bypass flap can also be integrated in the inlet region of the second fluid in such a way that, as required, the gas flow is directed directly into the bypass channel or into the heat exchanger channels. Even with such an integrated bypass flap, an additional separating element may be required between the start of the bypass and the flap for sealing. All described solutions can be provided with the same functionality in the exit region for the second fluid, ie separating element and bypass valve in the described arrangements and combinations. The statements regarding the required separation of the fluid flows in the supply line then apply accordingly to the discharge. All solutions are also possible with a combination valve instead of a bypass flap, that is, in addition to the steering of the fluid in the heat exchanger channels or in the bypass and the complete blockage of the second fluid is possible. For example, the described bypass valves or valves can be actuated via an electric actuator or via a U-can (pressure actuator).

The heat exchanger according to the invention allows for very different designs of the bypass channel. In a further development of the invention, the bypass in the stacking direction of the disk pairs is inserted below the lowermost disk or above the uppermost disk. It adjoins directly to the housing. In one embodiment of the invention, the bypass is inserted laterally next to the stacked disc pairs in the housing. In one development of the invention, the bypass channel is embodied in one piece with the housing by impressing one or more longitudinal corrugations in the housing in such a way that the bypass channel is formed which extends on one side from the housing wall and on the other side through the housing first disc of the disc bundle is limited. In one embodiment of the invention, a bypass is designed such that a substantially U-shaped shell placed on a side of the housing and in particular with this is joined and in particular with this soldered, welded, glued, etc is. In this case, the bypass between the attached shell and the housing wall is included. Furthermore, a heat exchanger according to the invention can also be combined with a completely external bypass, that is to say a closed flow channel for the second fluid, which can be connected to the heat exchanger, for example welded, soldered, or fixed in common holders with the heat exchanger. An external bypass can also be completely separated from the heat exchanger.

In a further development of the invention, any form of spacer between the disk stack and the housing wall can be used, such as a corrugated metal sheet or a ribbed sheet metal. Furthermore, permeable structures such as wire mesh, porous materials or the like are conceivable. Particularly advantageous may also be a longitudinally extending shell which has a U-profile and which opens to a housing wall. With the closed side she supports the disk stack.

In a development of the invention, the structures forming the channel protrude in the longitudinal direction over the heat exchanger channels formed by the stacked disks into the inlet and / or outlet region of the second fluid. In this way, a separating element between Bypassflu- idstrom and heat exchange fluid flow can be omitted. In one embodiment of the invention, the integrated bypass flap is designed such that no additional separating element for the bypass channel is required.

The bypass channel is to allow the passage of the second fluid past the heat exchanger channels without strong energy transfer from or to the first fluid and it should therefore be thermally decoupled from the first fluid as well as possible. The decoupling can be done for example by a knob or bead support of the bypass channel against the housing wall and / or against the disk stack. The nubs or beads can be made both from a structure forming the bypass channel, for example a tube and / or from the housing wall or the adjacent one first disk of the disk stack to be pronounced. As an insulating element, an additional insulation between the bypass channel and adjacent structures can be inserted, which has a low thermal conductivity (good insulation). The insulating effect is carried out by insulating materials and / or by the shaping, in particular by a rib structure.

In a further development of the invention, the bypass channel is made double-walled, in particular with a thicker, supporting outer wall and a thinner, inner wall. The two walls are designed such that the outer wall has lower thermal stresses than the inner wall.

In a further embodiment of the invention, it is provided that the heat exchanger can be flowed through in two or more flows, d. H. the second fluid is divided into sub-streams, which are each passed through a part of the heat exchanger channels in parallel or in countercurrent. For separating the partial flows, the same arrangements of separating plates and inlet / outlet openings can be used, as already described for the integration of the bypass tube.

In one embodiment of the invention, the partial exhaust gas streams are guided out of two cylinder banks each in a tide. Thus, the respective pressure spikes that result in the two floods can be used to increase the exhaust gas recirculation rate and the fuel efficiency, if a backflow into the other flood is avoided. The return flow is therefore prevented by check valves, which are integrated in the exhaust gas cooler in particular in the outlet region of the second fluid or arranged in combination with a separating plate in the outlet region at the outlet opening of the cooler housing, for example flanged.

In a development of the invention, multi-flow heat exchangers are formed with a deflection of the second fluid. In this case, the second fluid is not divided into sub-streams but through a portion of the fluid channels led from the inlet end of the second fluid to the other end, where it deflected, in particular substantially deflected by 180 °, and is returned by another part of the fluid channels again. The deflection can be done in several sub-stages. But it can also be provided several deflections, wherein the outlet of the second fluid takes place at an odd number of deflections at the inlet end of the heat exchanger and the outlet takes place at an even number of deflections at the other end of the heat exchanger.

In a further development of the invention, the deflection takes place as a U-flow, wherein the inlet and the outlet for the second fluid are close to each other at a radiator end, whereby the heat exchanger can be integrated space-optimized.

In a further development of the invention, the heat exchanger is designed as a charge air intermediate cooler between the compressor stages of a turbo engine, wherein in particular no separating elements or other deflecting elements are formed in the deflection region, since the deflection takes place by means of a housing closed at this end.

In a further development of the invention, no separate bypass pipe is required in the case of the U-flow design since the connection between the inlet and outlet nozzles in the combined inlet / outlet region of the cooler is short-circuited during bypass operation. In the case of cooled exhaust gas recirculation, the path between the inlet and outlet ports is blocked and the second fluid, in particular the exhaust gas, is guided through the heat exchanger channels.

In a development of the invention, the heat exchanger with U-flow is designed with an internal bypass flap and / or a combination valve and / or with an external bypass flap and / or with a combination valve. In the case of an external bypass flap in combination with a U-flow cooler, the division of the inlet / outlet area by a separating element is to be provided and the bypass flap is then integrated in particular in a module which can directly short-circuit the path through the exhaust gas cooler. As mentioned, the heat exchanger according to the invention can be used particularly advantageously as an exhaust gas cooler; In particular, the cooling of the housing shell is advantageous because the coolant is partially in direct contact with the housing wall or indirectly via material bridges with the housing wall in connection. The cooling of the exhaust gas cooler can be done depending on the application in a high or low pressure exhaust gas recirculation (exhaust extraction before or after the exhaust turbine) by the coolant of the cooling circuit of the engine or by air, with an adjustment of the flow cross sections and the heat transfer, z. B. is done by turbulence inserts. An advantage of the use as an exhaust gas cooler is also the arrangement of an oxidation catalyst in the flow direction of the exhaust gas in front of the disk pairs, ie in the inlet region of the exhaust gas cooler. Particularly useful is the integration of an oxidation catalyst in front of the heat exchanger tubes and an optionally required bypass flap in the outlet region of the radiator, since then the flap / combi valve is protected from contamination.

The heat exchanger according to the invention can also be used advantageously as a charge air cooler, whether with direct cooling (air) or with indirect cooling (liquid coolant). Furthermore, the heat exchanger according to the invention can be used advantageously as a coolant-cooled oil cooler or as an air-cooled condenser of an automotive air conditioning system. For the different uses, only adaptation to the different media and heat transfer conditions is required.

Furthermore, for the first medium, in addition to the two simple connection types, direct current between the first and second fluid or countercurrent between the first and second fluid (the U-flow cooler being a combination of both) may also be provided more than one circuit for the first fluid. Thus, for example, in an exhaust gas cooler application in the inlet region of the exhaust gas, the coolant flow can be conducted parallel to the exhaust gas, which effectively serves to prevent boiling, and in the outlet region of the exhaust gas, the coolant flow is conducted in countercurrent to the exhaust gas, whereby a particularly efficient heat transfer in the rear part of the heat exchanger is achieved, see DE10328746, whose is hereby expressly disclosed. The discharge of the first fluid in the middle of the heat exchanger can be done by a common exit for both circuits or by separate outlets. To improve the heat transfer, however, it is also possible, for example, for two circuits for the first medium to be arranged one behind the other and for both to flow in countercurrent to the second fluid. In this case, both circuits for the first medium have their own entrance and exit.

Concepts with two circuits of the first fluid countercurrent to the second fluid are particularly useful when first and second medium have similar heat capacities or the second medium has a higher heat capacity than the first, especially if both media are gaseous.

Embodiments of the invention are illustrated in the drawings and will be explained in more detail below. Show it

1 shows a section through an exhaust gas cooler according to the invention with disc-shaped coolant channels,

2a, 2b, 2c further embodiments for the formation of the coolant medium channels with direct cooling of the housing wall,

3a, 3b, 3c further embodiments for the formation of the coolant channels with indirect cooling of the housing walls, Fig. 4 is an exploded view of the exhaust gas cooler with housing shell, disc pairs and cover, Fig. 5a shows an exploded view of the disc pairs and the lid,

FIG. 5b shows an exploded view of an unfused disk pair, which comprises at least one upper disk and at least one lower disk, and another lower disk of an adjacent disk pair

Fig. 5c is a section C-C by an exploded view of an unfastened disc pair, which comprises at least one upper disc and at least one lower disc

Fig. 5d is a perspective view of a joined pair of discs Fig. 5e is a view of an assembled pair of discs in the flow direction of the second fluid

Fig. 6a, 6b, 6c forms of training for a two-part housing of the exhaust gas cooler, Fig. 7a, 7b longitudinal sections through the exhaust gas cooler with different

Exhaust and coolant guidance,

8a, 8b are longitudinal sections through the exhaust gas cooler with integrated bypass pipe and dividing wall in the inlet or outlet region,

9 shows a longitudinal section through an exhaust gas cooler with bypass pipe and integrated bypass flap,

10 is a longitudinal section through an exhaust gas cooler with bypass pipe and two separate inlet nozzle,

11 is a longitudinal section through an exhaust gas cooler with deflection of the exhaust gas flow (double-flow), Fig. 12 shows a longitudinal section through an exhaust gas cooler with double-flow

Flow and integrated bypass with bypass flap,

13 is a longitudinal section through an exhaust gas cooler with oxidation catalyst in the exhaust gas inlet region,

Fig. 14 is a longitudinal section through an exhaust gas cooler with two floods and one check valve for each flood in the outlet region of the 2 fluid

Fig. 15 is a longitudinal section D-D by two crimped and joined

Disk pairs and

16 is a longitudinal section through an exhaust gas cooler with deflection of the exhaust gas flow (double-flow), wherein the

Fluid enters the exhaust gas cooler in one tide and exits the exhaust gas cooler through the other.

1 shows a heat exchanger 1 according to the invention, which is designed as an exhaust gas cooler and can be used in an exhaust gas recirculation system (EGR system) of an internal combustion engine for motor vehicles. EGR systems are known from the prior art: in this case, the exhaust gas of the internal combustion engine is removed in front of or behind an exhaust gas turbine (high-pressure or low-pressure recirculation) and cooled in one or two stages to the intake tract of the internal combustion engine. The withdrawn amount of gas is controlled by an exhaust gas recirculation valve (EGR valve). The illustrated exhaust gas cooler 1 is traversed by exhaust gas and cooled by a liquid coolant, which is preferably removed from the cooling circuit of the internal combustion engine. The exhaust gas cooler 1 has a two-part housing 2, which consists of a trough-shaped housing shell 2a and a cover 2b - both parts are preferably formed as sheet metal parts and can be produced by deep drawing. In the housing shell 2a, a package of disc pairs 3 is arranged, which are flowed through by the coolant. The pairs of disks 3 extend over the full width of the housing shell 2 a, which has two housing walls 2 c, 2 d, which are shown perpendicularly in the drawing and run parallel to one another. The pairs of disks 3 have longitudinal sides 3a, which rest against the housing walls 2c, 2d, and form flow channels, which are equipped with turbulence inserts 4 to increase the heat transfer. The pairs of discs 3 are arranged in parallel at a distance from each other and form passageways 5 for the exhaust gas. In the passageways 5 turbulence inserts 6 are arranged to increase the heat transfer. All parts of the exhaust gas cooler 1 are cohesively, ie connected to each other by soldering. The soldering is preferably carried out in one operation in a soldering furnace, not shown. The disk pairs each have a top disk 80b and a bottom disk 80c.

Fig. 2a shows a further embodiment of the invention as a section of an exhaust gas cooler - for the same parts same reference numerals as in Fig. 1 are used. Between the two housing walls 2c, 2d two modified pairs of discs 7 are arranged, which are connected with their longitudinal sides 7a by soldering to the housing walls 2c, 2d. The pairs of disks 7 each consist of an upper disk 7b and a lower disk 7c, which are connected to each other at the edge via a fold. The flow cross-section through which the coolant flows reaches up to the housing walls 2c, 2d and thus effects cooling of the housing walls, which are heated by the exhaust gas stream.

FIG. 2b shows a further embodiment of the invention for the embodiment of a pair of discs 8, which consists of a top plate 8a, 80b and a lower plate 8b, 80c set together and laterally closed by a respective fold 8c. The flow cross-section of the pair of discs 8 is laterally expanded to side channels 8d, 8e, which have approximately the height of the exhaust ducts 5 and arranged in the exhaust ducts 5 turbulence inserts 6. The side channels 8d, 8e, which are flowed through by the coolant, thus extend from a pair of disks 8 to the adjacent pair of disks and lie over the entire surface of the housing walls 2c, 2d. As a result, a very good cooling of the housing walls 2c, 2d is achieved, which are thus isolated from the exhaust gas flow. Identical features are provided with the same reference numerals as in the preceding figures.

2 c shows a further embodiment of disk pairs 9, which comprises a top disk 80 b and a bottom disk 80 c, between housing walls 2 c, 2 d, wherein side channels 9 a, 9 b are formed by an enlargement of the flow cross-section, which, however, do not have the full height of the exhaust channels, but only a part, z. B. 50% - the remaining channel height is bridged by a longitudinal fold 9c, 9d. This embodiment also results in a very good cooling of the housing walls 2c, 2d, since they are surrounded by coolant. Identical features are provided with the same reference numerals as in the preceding figures.

FIGS. 3 a, 3 b, 3 c show further exemplary embodiments of the invention for embodiments of disk pairs 10, 11, 12 which are each formed from an outer disk 80 b and a lower disk 80 c whose flow channels have a width b which is smaller than that clear width w of the housing is - between the flow channels of the disk pairs 10, 11, 12 are each longitudinally extending material bridges 10a, 10b, 11a, 11b, 12a, 12b arranged, which - each in different configurations - on the housing walls 2c, 2d abut and soldered with these. As a result, a good cooling effect, ie an indirect cooling of the housing walls 2c, 2d is also achieved, ie by heat conduction via the material bridges 10a, 10b, 11a, 11b, 12a, 12b. Identical features are provided with the same reference numerals as in the preceding figures. 4 shows a 3D representation of the individual parts of an exhaust gas cooler, which corresponds to the exemplary embodiment according to FIG. Identical features are provided with the same reference numerals as in the preceding figures. In the drawing below, a trough-shaped housing shell 13 is shown, which end face, ie on its narrow side an exhaust gas inlet opening 13a and on the opposite narrow side (largely hidden) has an exhaust gas outlet opening 13b. Above the housing shell 13, three pairs of disks 14, a cover plate 15 and the housing cover 16 are shown. The approximately rectangular shaped pairs of discs 14 have on their longitudinal sides in each case angled edge strips 14a, which are formed as folds and can be soldered to the inside of the housing shell 13. The disk pairs 14 are flowed through by coolant and therefore have cup-like characteristics 14b, 14c, which in the soldered state in each case form a feed and a discharge channel for the disk pairs, which can thus be flowed through parallel to one another. The coolant connections (not shown here) are located in the lid 16 of the housing. It can also be seen from this illustration that the individual parts of the exhaust gas cooler can be easily joined and prepared for the soldering process.

FIG. 5a shows a further illustration of the pairs of disks 14 according to FIG. 4 in a front view, ie viewed in the flow direction of the exhaust gas. The same reference numerals as in Fig. 4 are used. The pairs of disks 14 are arranged parallel and at a distance from each other and form approximately rectangular flow channels (passage channels) 17 for the exhaust gas, in which case turbulence inserts, as shown in Figures 1 to 3, are omitted. The pairs of discs 14 each consist of two discs, namely an upper disc 14d and a lower disc 14e, which are connected to each other at their longitudinal sides by the angled fold 14a. The end faces 14f, which form the leading edges for the exhaust gas, in contrast, are connected to each other by a shallow fold. Thus, the pairs of discs 14 are peripherally sealed circumferentially. The cup-like characteristics 14b are formed from the upper disk 14d and abut on the adjacent lower disk 14e - thus becomes a transverse to the exhaust gas flow direction inlet and outlet channel for the coolant created. The characteristics are aerodynamically designed to achieve a low exhaust gas pressure drop, z. B. - as shown in Fig. 4 can be seen - with an oval or elliptical cross-section. Incidentally, depending on the application, instead of the turbulence inserts, structural elements in the form of beads or so-called winglets can also be molded into the panes.

FIG. 5 b shows an exploded view of an unfused disk pair 3, 14, which comprises at least one upper disk 80 b and at least one lower disk 80 c, as well as a further lower disk 80 c of an adjacent disk pair. Identical features are provided with the same reference numerals as in the preceding figures. The upper disc 80b and the lower disc 80c each have a disc opening 81 formed as a bore. The upper disk 80b comprises at least one embodiment 14b, in particular two configurations 14b, which are formed as a truncated cone in the stacking direction. The truncated cone comprises on the side of the smallest outer diameter a Oberscheibenringfläche 82, 82 c, which is arranged parallel to the disc surface 92 of the upper disc 80 b and the lower disc 80 c and perpendicular to the stacking direction of the disc pairs 3, 14. The lower disk 80c has a lower disk ring surface 83, 83c, which is formed in one piece with the disk surface 92 and is identical to the disk aperture in the region of the disk opening. In the joined, in particular soldered, welded, bonded, etc. state, the upper disc ring surface 82, 82c of a disk pair 3, 14 and the lower disk ring surface 83, 83c of an adjacent disk pair 3, 14 touch each other and are connected to one another in a materially bonded manner. The upper disk 80b comprises at the disk edges an upper disk edge surface 85. The lower disk 80c comprises at the disk edges a lower disk edge surface 86. The outer disk surface 85 and lower disk edge surface 86 correspond to each other and are materially bonded, in particular by soldering, welding, gluing etc. The upper disk edge surface 85 extends in the longitudinal direction of the disk substantially parallel to the signing edge surface 86, as well as the upper disk edge surface 85 in the direction of the disk width which, in particular substantially perpendicular to the longitudinal direction of the disk and substantially perpendicular to the Stapelrich- is aligned with the discs, substantially parallel to the lower edge of the disc. In the sections of the top edge surface and the bottom edge surface in which the longitudinal side of the pane merges into the width of the pane in the stacking direction, a joint 93 of the bottom and top edge surface is formed so that the impact 93 of a pane edge surface is substantially longitudinal is designed as a quarter-cylinder and that touch the quarter-cylinder of the lower and upper disc substantially like two telescoped concentric quarter cylinder and are materially connected, in particular by soldering, welding, gluing, etc.

FIG. 5c shows a section C-C through the exploded illustration FIG. 5b of an unfused disk pair, which comprises at least one upper disk 80b and at least one lower disk 80c. Identical features are provided with the same reference numerals as in the preceding figures.

Fig. 5d shows a perspective view of a joined pair of discs 3, 14. The same features are provided with the same reference numerals as in the preceding figures. In the joined, in particular soldered, welded, glued, etc. state, the Oberscheibenring- surface 82, 82c of a disc pair 3, 14 and the lower disc ring surface 83, 83c of an adjacent disc pair 3, 14 touch and are connected to each other cohesively. The upper disk 80b comprises at the disk edges an upper disk edge surface 85. The lower disk 80c comprises at the disk edges a lower disk edge surface 86. Oberscheibenrandfläche 85 and lower disk edge surface 86 correspond to each other and are cohesively, in particular by soldering, welding, gluing, etc. interconnected. The upper disk edge surface 85 extends in the longitudinal direction of the disk essentially parallel to the signing edge surface 86, as well as the upper disk edge surface 85 in the direction of the disk width which, in particular substantially perpendicular to the longitudinal direction of the disk and is oriented substantially perpendicular to the stacking direction of the disks, substantially parallel to the lower disk edge surface , In the sections of the upper edge surface and the lower edge surface, in which the longitudinal side of the disc in the stacking direction in the disc Width transitions, a shock 93 of the bottom and top plate edge surface is formed such that the impact 93 of a disc edge surface in the longitudinal direction is substantially formed as a quarter cylinder and that the quarter-cylinder of the lower and upper disc substantially as two nested concentric quarter cylinder touch and cohesively, in particular by soldering, welding, gluing, etc. are connected.

FIG. 5e shows a view of a joined pair of disks in the flow direction of the second fluid. Identical features are provided with the same reference numerals as in the preceding figures.

Fig. 6a, 6b, 6c show different shapes for the formation of housings 17, 18, 19, each having box-shaped or trough-shaped housing shells 17a, 18a, 19a. Identical features are provided with the same reference numerals as in the preceding figures. Different are the lid forms 17b, 18b, 19b. The cover 17b has a circumferential bead (channel) 17c, which can be placed on the peripheral upper edge of the housing shell 17a and thus soldered. The lid 18b has an upstanding peripheral edge 18c, which rests against the inner wall of the housing shell 18a. The cover 18b can thus "sag" during soldering (during melting of the solder layers of the disk package.) The cover 19b has an angled edge 19c which surrounds the upper edge of the housing shell 19a on the outside and can thus be soldered all around Deep-drawn parts can be produced.

7a shows an exhaust gas cooler 20 in longitudinal section with a housing 21 consisting of housing shell 21a, cover 21b, an inlet of the first fluid 90 and an outlet of the first fluid 91. In the housing 21 is a packet 22 (shown hatched) , consisting of the previously mentioned, not shown here disc pairs, which are traversed by the coolant arranged. Identical features are provided with the same reference numerals as in the preceding figures. The respective coolant connections are arranged as sockets 23, 24 in the cover 21 b of the housing 21. The exhaust gas, represented by arrows A, passes through a livestock In the exhaust gas flow direction in front of the disk pack 22, an inlet region 27 is left, which acts as a diffuser, and downstream of the disk pack 22, an outlet region 28 is left in the housing 21, which in the outlet nozzle 26 passes. The exhaust gas, represented by the arrows A, thus flows essentially in the longitudinal direction ("axially") through the exhaust gas cooler 20 or the disk pack 22.

Fig. 7b shows a similar exhaust gas cooler 29 with the difference that the coolant connections 30, 31 are arranged in the bottom part of the radiator and the outlet side exhaust nozzle 32 in the cover part of the housing, whereby a 90 degree deflection of the exiting exhaust gas, represented by an arrow A, accessible is. Identical features are provided with the same reference numerals as in the preceding figures. Such changes in the exhaust and Kühlmittelzu- or removal are thus possible by simple measures on the housing. In FIGS. 7a, 7b exhaust gas and coolant flow are shown as direct current. However, it is also possible to carry both media in countercurrent to each other.

FIGS. 8a and 8b show further exemplary embodiments of the invention, namely an exhaust gas cooler 33 with a bypass channel 34 arranged at the bottom and an exhaust gas cooler 35 with a bypass channel 36 arranged on top. Identical features are provided with the same reference symbols as in the preceding figures. Both bypass channels 34, 36 may be formed as a tube and are inserted into the housing, in each case parallel to the hatch packages 37a, 37b shown hatched. The exhaust gas cooler 33 according to FIG. 8a has a separating or sealing element 38 in the exhaust gas inlet region, which serves to separate the exhaust gas stream into two partial streams for the disk package 37a on the one hand and the bypass pipe 34 on the other. The exhaust gas cooler 35 according to FIG. 8b has an exhaust gas feed with a 90 degree deflection from the cover side - accordingly an angled separating element 39 is arranged in the exhaust gas inlet region, which seals the exhaust gas partial flows against one another. In both cases, an unillustrated bypass valve is thus arranged outside of the exhaust gas cooler. FIG. 9 shows, as a further exemplary embodiment of the invention, an exhaust gas cooler 40 with disk pack 41 and bypass duct 42 arranged therebelow, wherein a pivotable bypass flap 43 is arranged in the exhaust gas inlet region, represented by the exhaust gas arrow A. Identical features are provided with the same reference numerals as in the preceding figures. Thus, the exhaust stream can be directed either through the disk pack 41 or through the bypass channel 42, with intermediate positions are possible. The design of a bypass flap is known from the prior art, also under the term exhaust manifold.

FIG. 10 shows, as a further exemplary embodiment of the invention, an exhaust gas cooler 44 with a disk pack 45 (heat exchanger part) and a bypass duct 46 arranged at the top, to which separate exhaust gas inlets 47, 48 in the housing of the exhaust gas cooler 44 are assigned. Identical features are provided with the same reference numerals as in the preceding figures. Between the two exhaust gas inlets 47, 48, a separating element or a partition wall 49 is arranged, which can be soldered to the housing.

Fig. 11 shows a further embodiment of the invention, a double-flow exhaust cooler 50 with a disk pack 51 (heat exchanger part), an exhaust gas inlet chamber 52, a partitioned by a partition exhaust outlet chamber 53 and a deflection chamber 54 for the exhaust stream, represented by a long-drawn, U-shaped trained arrow A. Same features are provided with the same reference numerals as in the preceding figures.

FIG. 12 shows a further exemplary embodiment of the invention, namely a double-flow exhaust gas cooler 55 which has an exhaust gas chamber 56 with an exhaust gas inlet connection 57 and an exhaust gas outlet connection 58. Identical features are provided with the same reference numerals as in the preceding figures. In the exhaust chamber 56, a pivotable exhaust flap 59 (solid line) is arranged, which in a dashed position shown 59 'is pivotable. In position 59, inlet connection piece 57 and outlet connection pieces 58 are separated from one another, ie the discharge Gas stream flows through the heat exchanger part 60 in accordance with the arrow A shown in U-shape and exits through the exhaust pipe 58; the entire exhaust stream is thus cooled. In the event that no exhaust gas cooling is required, the exhaust flap 59 is moved to the position shown in dashed lines 59 ", so that the entering into the inlet port 57 exhaust gas flow is direct - in the short -in the outlet nozzle 58 and from the exhaust gas cooler 55th The exhaust gas chamber 56 thus forms a bypass channel, represented by a dashed arrow B. The disk package 60 can thus be bypassed in the bypass 16. The exhaust gas cooler 55 thus has an integrated bypass with integrated bypass flap.

FIG. 13 shows, as a further embodiment of the invention, an exhaust gas cooler 61 with a heat exchanger part 62 (disk package) which can be flowed through by exhaust gas ("axially") corresponding to the exhaust gas pipes A. The same features are denoted by the same reference numerals as in the preceding FIGS The exhaust gas cooler 61 has an exhaust gas inlet region 63 in the form of a diffuser, in which an oxidation catalytic converter 64 is arranged which, as is known from the prior art, serves for exhaust gas purification in that a rectification of the exhaust gas flow and thus an improved loading of the downstream disk pack 62 can be achieved by the exhaust ducts, not shown, of the oxidation catalytic converter.

Fig. 14 shows a longitudinal section through an exhaust gas cooler with two floods and one check valve for each flood in the outlet region of the second fluid. Identical features are provided with the same reference numerals as in the preceding figures. A first flow 87 of the second fluid, which is designed in particular as a bypass, and a second flow 88 of the second fluid enter into the inlet region of the second fluid into the heat exchanger. The first flood 87 and the second flood 88 are separated by a separating wall-shaped sealing member 89 from each other sealingly. The sealing element 89 is aerodynamically designed for the second fluid in such a way that the floods which enter the heat exchanger in an oblique manner relative to the longitudinal direction of the disk are conveyed through the radiused sealing element. ment to the entry in the disc package in the disc longitudinal direction ϋ- be transferred. In particular, in the outlet region of the heat exchanger, a first check valve 94 for the first flood and a second check valve 95 for the second flood integrated and formed such that the first check valve 94 includes a first pivot 98 adjacent to the housing bottom, which pivotal movement of a first valve flap 96 to an axis of rotation, which is arranged parallel to the disc width and perpendicular to the disc longitudinal direction, allows. The second check valve 95 comprises a second pivot 99, which is arranged adjacent to the housing cover and a pivoting movement of a second valve flap 97 about an axis of rotation, which is arranged parallel to the disc width and perpendicular to the disc longitudinal direction allows. A backflow of the second fluid from the exit region back into the disk package is thus prevented.

Fig. 15 shows a longitudinal section DD through two verkrimpte and joined pairs of discs. Identical features are provided with the same reference numerals as in the preceding figures. The upper disks 80b and the lower disks 80c are arranged substantially parallel to one another, the distance between a upper disk 80b and a lower disk 80c of a disk pair 3, 14 being the height of the flow channel for the first fluid and the distance between a lower disk 83 and the upper disk 82 of an adjacent disk pair forms the height of the passageway for the second fluid. The lower discs 81c are formed with an opening 81 about which a lower disc ring surface 83 is formed concentrically. The upper disks 81b also have an opening 81. In the region of these openings, conical shapes 14b are formed conically perpendicular to the disk surface and in the stack disk direction from the upper disks. In the section of the expression 14b of the smaller of the two cone diameters, which are located at the two cone ends, the expression buckles and runs parallel to the disk surface, whereby an upper disk ring surface 82 is formed, which touches the washer surface 83 of an adjacent disk pair and materially , in particular by soldering, welding, gluing, etc. is connected thereto. The Oberscheibenknicken beyond the forms 14b in Direction of the inlet region for the second fluid in the direction of the housing bottom from. The height of the flow channel decreases until the upper disk 80b and the lower disk 80c of a pair of disks touch and extend parallel to one another and are connected to one another in a material-locking manner, in particular by soldering, welding, gluing etc. The lower plate 80c projects slightly beyond the length of the upper plate 80b in the longitudinal direction, resulting in an end width region 101 of the lower plate 80c, which is bent around the associated upper plate 80b of the plate pair 3, 14, at least in sections over the entire width of the plate, and thus engages around the upper plate , which is called crimping. The crimping also reduces the flow losses when the second fluid flows onto the pairs of discs in comparison to the flow onto an edge. In the same way, the lower disks with the upper disks are at least partially crimped over the entire disk width on the exit side of the disk package, which however is not shown in FIG. The crimping takes place at least in sections also over the two longitudinal sides of the discs, which is likewise not shown in FIG. In a further embodiment, not shown, the upper disk can engage around the lower disk.

Fig. 16 shows a longitudinal section through an exhaust gas cooler with deflection of the exhaust gas flow (double-flow), wherein the fluid enters the exhaust gas cooler in a flood and exits through the other flood from the exhaust gas cooler. Identical features are provided with the same reference numerals as in the preceding figures. The inlet and outlet for the second fluid are on the same side of the heat exchanger. They are separated by a sealing element 89, which is designed as a wall, sealingly from each other. The second fluid flows through the inlet exit region into the heat exchanger, the deflection takes place as a U-flow, and the second fluid flows countercurrently to the outlet region and leaves the heat exchanger. The inlet and the outlet for the second fluid are arranged close to each other at a radiator end, whereby the heat exchanger can be integrated space-optimized. The turbulence-generating elements or the turbulence inserts are formed in a further embodiment, not shown, as rib ribs.

Turbulence inlays with ribbed ribs have a relatively low tendency to accumulate deposits, in comparison to other inlays, in comparison with other liners, with smaller passage cross sections. Basically, it was to be feared that turbulence inserts with rib ribs would increasingly lead to the blocking of individual passageways due to the delicate structure of the rib ribs. However, this is the case to a surprisingly small extent, in particular if the webs of the rib ribs are relatively short. A possible explanation for this could be that due to the turbulent flow of the exhaust gas present over large portions of the ribbed insert, particle deposits are reduced, whereas in the case of longer, uniform channels, ordered flows are formed near the wall due to the very low flow velocity Favor particles.

To the figures 1 to 16

In a preferred embodiment, the webs of the rib ribs have a length which is not more than about 10 mm, preferably not more than about 5 mm and particularly preferably not more than about 3 mm. Depending on the space available and the internal combustion engine, there may be specific requirements for the pressure drop at the exhaust gas heat exchanger. Depending on these requirements, one of the aforementioned length ranges may be preferred.

Further preferably, a density of the rib ribs transverse to the exhaust gas flow direction is between about 20 rib ribs / dm and about 50 rib ribs / dm, preferably between about 25 rib ribs / dm and 45 rib ribs / dm. These Stegripendichten have been found in experiments to be particularly suitable. In particular, the rib ribs particularly advantageously represent a good compromise between blocking risk and cooling performance. With regard to a height of the rib ribs, it should be taken into account that at relatively high altitudes only relatively small primary surfaces, ie surfaces cooled by coolant, are available, via which the entire heat must be released into the coolant. With relatively small primary surfaces, the boil risk increases in the case of a liquid coolant. In addition, the efficiency of the deposits decreases with increasing height of the rib ribs. A preferred height of the insert or Stegrippe is therefore between about 3.5mm and about 10mm, more preferably between about 4mm and about 8mm and more preferably between about 4.5mm and about 6mm.

In a preferred embodiment of the device according to the invention, it can be provided that an oxidation catalytic converter is arranged in front of the plurality of flow channels. By such a catalyst can be generally reduce the particle sizes, particle densities and the proportions of hydrocarbons in the exhaust gas by oxidation. It may be additionally or alternatively provided that the deposits themselves are provided with a coating for the catalytic oxidation of the exhaust gas. Particularly in connection with oxide catalytic agents, the useful density of the rib ribs transverse to the direction of the exhaust gas flow can be more than about 50 ribs / dm, in particular about 75 ribs / dm. As a result, a particularly large heat exchanger capacity would be achieved with a given installation space without the long-term danger of deposits being blocked.

In a particularly preferred embodiment, the rib ribs are helically toothed. Helical ribs are according to experimental findings particularly suitable to ensure a long-term stability of the exhaust gas heat exchanger against deposits. In this case, in a preferred embodiment, the angle between the web walls and a main direction of the rib ribs between about 1 ° and about 45 °. In a particularly preferred embodiment, the angle between about 5 ° and about 25 °, where it may be in an alternative preferred embodiment, between about 25 ° and about 45 °. The first-mentioned value range 5 ° to 25 ° is particularly well suited for typical applications which are sensitive to pressure loss, with the second range of values being used to achieve an optimized pressure loss Power density, especially for less pressure loss sensitive applications.

In general, a correlation between the angle of the walls and a longitudinal division of the ribbed rib can be determined when optimizing an insert with obliquely toothed ribs. In particular, optimal designs at small angles may have larger pitches I than optimized designs with large angles. Particularly with small angles of attack, designs with moderate pressure loss can result. Particularly with large angles of attack, designs with optimized power density can result. In particular, with small angles of attack, the longitudinal pitch can be greater, with large angles of attack, the longitudinal pitch can be smaller in particular to obtain optimized versions.

In a preferred embodiment, the device is designed as a stacked plate heat exchanger. Both in terms of the width of a flow channel as well as in terms of cost-effective production and combinability of a heat exchanger housing with ribbed ribbed inserts, this embodiment is particularly suitable. Alternatively, the device can also be designed as a tube bundle heat exchanger or as another known per se heat exchanger.

In general, the insert is preferably made of a stainless steel, in particular an austenitic steel, in order to prevent corrosion caused by the aggressive exhaust gas.

In a further advantageous embodiment, aluminum materials can be used, in which case a suitable corrosion protection can be provided in a particularly advantageous manner, such as in particular an alloy and / or a coating.

In an advantageous development, the insert is formed of aluminum. The insert made of aluminum has a particularly low weight. special Advantageously, the insert may be formed of aluminum by means of an alloy or coating for corrosion protection.

Depending on the flow parameters, in particular the Reynolds number, the length of the inlet region of the flow channels, in particular tubes and / or stacking disk pairs, l / s about 2.5 to 5 and the length of the rib ribs must be selected below this limit. S denotes the mean passage width between two webs and is thus b / 2-t, where t denotes the sheet thickness. The result is a required ratio l / s <4, in particular l / s <2. For high blocking risk by critical exhaust gas composition l / s <1, 5, in particular l / s <1 to choose.

By an inclination of the webs occurs on the swirl side, a higher flow velocity on the wall, which counteracts the soot deposition. Another decisive advantage of helical rib ribs is that in cases where a low density of the rib ribs in the transverse direction of flow is required for Verlockungsvermeidung, especially in unfavorable exhaust gas composition, despite a small rib surface sufficient cooling performance can be guaranteed.

The stacked-plate heat exchanger according to the invention comprises an outer housing with a cover, wherein an inlet and an outlet are provided for the exhaust gas and an inlet and an outlet for a liquid coolant. Within the housing, a plurality of disc elements are provided, each of the disc elements being composed of an upper half and a lower half. By means of turned-on collar, the disc elements are welded to one another and to the housing so that the coolant flows in each case between the two halves of a disc element from the inlet to the outlet. Between two disc elements in each case a not shown inlay with rib ribs is arranged, wherein the intermediate space between two disc elements in each case forms a flow channel for the exhaust gas. The deposits are not shown in the interest of clarity. The inserts are made of stainless steel. To improve the thermal contact between the inserts and the disc elements or the housing, the inserts can be welded or soldered flat with said elements.

In a further embodiment, the turbulence insert consists of a thin sheet metal material into which parallel rib ribs are introduced by means of forming measures. Each of the rib ribs comprises a series of webs successively arranged in the exhaust gas flow direction. In each case two webs, which follow each other in the exhaust gas flow direction, are arranged offset from one another by half a web width transversely to the exhaust gas flow direction, so that after each web a cutting edge adjoins a subsequent web. In the present example, the walls are aligned parallel to the flow direction of the exhaust gas and form with an axis B of the rib ribs and the main flow direction of the exhaust gas A at an angle of 0 °. Such ribbed insert is referred to as a straight-toothed rib.

In the first embodiment, the length I of a ridge is about 4mm. The width b of a single rib is defined as the width of the repeat unit of the periodic structure transverse to the main flow direction of the exhaust gas. The Stegrippendichte 2 / b is in the present example about 40 Stegrippen / dm. The width b of a Stegrippe is thus about 5mm

The height h of the rib ribs corresponds to the distance between two adjacent disc elements of the heat exchanger and is presently about 5 mm.

In a further embodiment of the ribbed ribbed insert, the lateral walls of the individual ribs are not aligned parallel to the main direction B of the rib ribs. Rather, each of the walls of the webs with the main direction B of the rib ribs includes an angle W of about 30 °. The other dimensions of the helical ribbed insert correspond to the dimensions of the straight-serrated ribbed rib.

Suitable longitudinal pitch I for corresponding angles of the walls W provide suitable designs at 10 ° with longitudinal pitches I <approximately 10 mm, at 20 ° with I <approximately 6 mm, at 30 ° with l <ca. 4mm and at 45 ° with l <about 2mm. The minimum longitudinal pitch I is approximately 1 mm at all angles. The permissible channel extension l / s is approximately within the same limit as for a straight toothed rib, where s denotes the web spacing transverse to the main flow direction B. As a rule, longitudinal divisions I <1 mm are difficult to produce for manufacturing reasons.

The at least one heat exchanger is at least one exhaust gas heat exchanger and / or a charge air cooler and / or an oil cooler and / or a coolant condenser and / or a refrigerant condenser for an air conditioner and / or a gas cooler for an air conditioner and / or a refrigerant evaporator for an air conditioner and / or a cooler for cooling electronic components.

In a first embodiment, the intercooler and / or exhaust gas cooler is a direct intercooler and / or direct exhaust gas cooler. Direct is to be understood that at least one medium to be cooled, such as exhaust gas and / or charge air is cooled directly by a cooling medium such as air.

In a second embodiment, the intercooler and / or exhaust gas cooler is an indirect intercooler and / or indirect exhaust gas cooler. Indirectly, it is to be understood that at least one medium to be cooled, such as exhaust gas and / or charge air is cooled by a coolant, such as a water-containing fluid and / or a liquid, such as cooling water, this water-containing fluid and / or the liquid as cooling water by a other cooling medium as ambient air is cooled.

The at least one charge air cooler is in another embodiment directly and the at least one exhaust gas cooler is cooled indirectly, or conversely, the at least one charge air cooler in another embodiment indirectly and the at least one exhaust gas cooler is cooled directly.

To improve the heat transfer, in a further embodiment at least two circuits, in particular two, three, four or more than four circuits, for the first medium in succession, ie in particular in the direction A and / or in the stacking direction, in which the discs are stacked , which in particular an angle of 0 ° to 90 ° with the direction A forms, are arranged. For example, the two, three, four or more than four circuits are flowed through in counterflow or in cocurrent or at an angle of 0 ° to 90 ° to the second fluid, in particular to the flow direction of the second fluid.

If the at least two circuits, in particular two, three, four or more than four circuits, for the first medium in succession, i. are arranged in particular in the direction A, at least initially a high-temperature circuit is arranged in the direction A flowing, which has a higher temperature than an at least second low-temperature circuit. In particular, the temperature difference between high-temperature and low-temperature circuit 10K to 100K, in particular 3OK to 8OK, in particular 3OK to 6OK.

The Hochtempertaturkreislauf has in particular in the operating condition temperatures between 70 ° C to 100 ° C, in particular between 80 ° C and 95 ° C. The low temperature, in particular in the operating state temperatures between 10 ° C and 7O ⁰ C _1, in particular between 20 ⁰ C and 6O ⁰ C, in particular between 30 ⁰ C and 65 ° C, in particular between 40 ⁰ C and 50 ⁰ C.

In this way, the recirculated exhaust gas and / or the charge air or at least one medium to be cooled is cooled in two, three, four or more stages.

The at least two circuits, in particular two, three, four or more than four circuits, for the first medium are designed as at least one U-flow circuit and / or as at least one I-flow circuit. For example, at least two I-flow circuits or at least two U-flow circuits are arranged in series, in particular one after the other. In another example, at least one U-flow cycle follows at least one I-flow cycle or vice versa. In particular, in the arrangement of at least two U-flow circuits, the coolant connections for the at least two circuits in one example are on one side of the radiator, for example arranged in the stacking direction of the discs above or below or to the stacking direction at an angle between 0 ° to 90 °.

In another example, the outflow takes place in the at least one high-temperature circuit and the backflow in the at least one Niderte- perturkreislauf or vice versa.

Furthermore, in another embodiment, a combination valve in the at least one heat exchanger, for example in the exhaust gas heat exchanger and / or in the at least one charge air cooler and / or in the at least one oil cooler and / or in the at least one coolant radiator and / or in the at least one refrigerant condenser integrated for an air conditioner and / or in the at least one gas cooler for an air conditioner and / or in the at least one refrigerant evaporator for an air conditioner and / or in the at least one cooler for cooling electronic components, in particular integrated into the housing of the heat exchanger, and / or formed in one piece with this. The combination valve combines the function of at least one exhaust gas recirculation valve for controlling and / or regulating the recirculated exhaust gas or exhaust air mixture and / or the function of at least one bypass valve, in particular a bypass valve, for bypassing recirculated exhaust gas to the at least one heat exchanger, in particular the exhaust gas heat exchanger and / or one of the other heat exchangers mentioned above, so that recirculated medium, in particular exhaust gas and / or air, is not cooled in the at least one heat exchanger, in particular exhaust gas heat exchanger and / or one of the other heat exchanges mentioned above. Such a combination valve is described in unpublished DE 10 2005 034 136.5, unpublished DE 10 2005 041 149.5, unpublished DE 10 2005 041 150.9, unpublished DE 10 2005 034 135.7 and in published DE 103 21 636, published DE 10321637 and US Pat published DE 10 2005 041 146, the entire contents of which are hereby expressly disclosed. The features of the various embodiments can be combined with each other. The invention can also be used for other than the areas shown.

Claims

Patent claims

1. Heat exchanger with flow channels, which can be traversed by a common first inlet to a common first outlet of a first fluid, with a housing which receives the flow channels in and of a second fluid, which differs from the first fluid, ( alternatively, and from a second fluid different from the first fluid) from a second inlet region to a second outlet region, wherein the flow channels have a flat cross section and longitudinal sides, characterized in that the longitudinal sides (3a) of the flow channels (3 ) are materially connected, in particular by soldering, welding, gluing, etc. with the housing (2).

2. Heat exchanger according to claim 1, characterized in that the flow channels (3) over the longitudinal sides (3a) substantially cohesively over its entire length with the housing, in particular by soldering, welding, gluing, etc. are connected.

3. Heat exchanger according to claim 1 or 2, characterized in that the flow channels as a pair of discs (3, 7, 8, 9, 10, 11, 12, 14) are formed and in connection with the housing (2) passageways (5) for form the second fluid.

4. Heat exchanger according to one of the preceding claims, characterized in that the flow channels (3) and the Durchtrittska- Ducts (5) are received substantially in their entirety by the housing (2).

5. Heat exchanger according to one of the preceding claims, characterized in that between a cover (2b, 16, 17b,

18b, 19b) and a lid adjacent the lid (7c, 80c) at least one flow channel (3) for the first fluid is formed.

6. Heat exchanger according to one of the preceding claims, character- ized in that between a to a bottom portion of a housing shell (2a, 13) adjacent upper disc (80b, 7b) and between the bottom portion of the housing shell (2a, 13) at least one flow channel (3 ) is formed for the first fluid.

7. Heat exchanger according to one of the preceding claims, characterized in that the pairs of discs (3, 7, 8, 9, 10, 11, 12, 14) has a lower and an upper disc (7b, 7c, 14d, 14e, 80b, 80c ), which are peripherally connected by a fold (3a, 7a, 8c, 14a) with each other.

8. Heat exchanger according to one of the preceding claims, characterized in that at least one inflow channel and / or at least one outflow channel extends transversely through the pairs of discs (14).

9. Heat exchanger according to one of the preceding claims, characterized in that the disc pairs (14) have at least one cup or at least one expression (14b).

10. Heat exchanger according to one of the preceding claims, characterized in that the expression (14b) of a disc pair (14) extends to an adjacent pair of discs, this touches and in particular with the adjacent disc pair is materially connected by soldering, welding, gluing, etc.

11. Heat exchanger according to one of the preceding claims, characterized in that the expression (14b) in the upper disc (80b) is introduced and the expression (14b) has a Oberscheiben- ring surface (82) which a lower disc ring surface (83) of the lower disc ( 80c) touches an adjacent pair of discs and in particular is materially connected by soldering, welding, gluing, etc. with the lower disc ring surface.

12. Heat exchanger according to one of the preceding claims, character- ized in that an expression in the lower pane

(80c) is introduced and the expression has a lower disc ring surface (83c), which touches a Oberscheibenringfläche (82c) of the upper disc (80b) of an adjacent disc pair and in particular materially by soldering, welding, gluing, etc. with the Oberscheibenringfläche (82c) is connected.

13. Heat exchanger according to one of the preceding claims, characterized in that the flow channels (3) are stacked.

14. Heat exchanger according to one of the preceding claims, characterized in that the cover (2b, 16, 17b, 18b, 19b) in the stacking direction on the housing (2) or the housing shells (2a, 13, 17a, 18a, 19a) placed is.

15. Heat exchanger according to one of the preceding claims, characterized in that the upper disc (80b) of a disc pair (14) has a top disc edge surface (85) and the associated lower disc (80c) has a lower disc edge surface (86), wherein the upper disc edge surface (85) the bottom edge surface (86) corresponds and cohesively, in particular by

Soldering, welding, gluing, etc. is connected.

16. Heat exchanger according to one of the preceding claims, characterized in that longitudinal sides (3a) of two flow channels (3) forming pairs of discs (14) at least be rich, in particular on the entire disc length, engage around and in particular that the housing contacting the longitudinal side (3a) the longitudinal side (3a) of an adjacent disc, in particular the other disc of the respective disc pair engages around.

17. Heat exchanger according to one of the preceding claims, characterized in that engage broad sides of two flow channels (3) forming pairs of discs (14) at least partially, in particular on the entire disc width.

18. Heat exchanger according to one of the preceding claims, characterized in that the pairs of discs (14) turbulence generating means (4), in particular turbulence inserts or embossed structural elements which are arranged in the flow channels (3).

19. Heat exchanger according to one of the preceding claims, characterized in that the characteristics (14 b, 84) are conical.

20. Heat exchanger according to one of the preceding claims, characterized in that the characteristics (14b, 84) in the direction of the longitudinal sides (14a) are streamlined, in particular formed with an elongated or elliptical cross-section.

21. Heat exchanger according to one of the preceding claims, characterized in that between flow channels or in the passage channels (5) turbulence generating means (6), in particular turbulence inserts or from the disc pairs (3, 7, 8, 9, 10, 11, 12) formed structural elements are arranged.

22. Heat exchanger according to one of the preceding claims, characterized in that the pairs of discs (3, 7, 14) via their longitudinal fold connections (3a, 7a, 14a) to the housing (2, 2c, 2d) are connected.

23. Heat exchanger according to one of the preceding claims, characterized in that the inlet region (27) of the housing (21) in the flow direction of the second fluid (A) in front of the Scheibenpaa- ren (22) is arranged.

24. Heat exchanger according to one of the preceding claims, characterized in that the outlet region (28) of the housing (21) in the flow direction of the second fluid (A) behind the disc pairs (22) is arranged.

25. Heat exchanger according to one of the preceding claims, characterized in that the pairs of disks (3, 7, 8, 9, 10, 11, 12, 14) of the second fluid substantially parallel to their longitudinal sides (3a, 7a, 14a) are flowed around ,

26. Heat exchanger according to one of the preceding claims, characterized in that the longitudinal fold (3a, 14a) by the same direction angled edges of upper and lower plate (14d, 14e) is formed and a contact surface for the housing (2, 2c, 2d) forms.

27. Heat exchanger according to one of the preceding claims, characterized in that the longitudinal fold (7a) by oppositely angled edges of the upper and lower plate (7b, 7c) is formed and forms a contact surface for the housing (2c, 2d).

28. Heat exchanger according to one of the preceding claims, characterized in that the disk pairs (8, 9) on the longitudinal side in the region of the housing walls (2c, 2d) side channels (8d, 8e, 9a, 9b) for the first fluid.

29. Heat exchanger according to claim 28, characterized in that the side channels (8d, 8e, 9a, 9b) are formed as an extension of the flow cross-section of the disk pairs (8, 9).

30. Heat exchanger according to claim 29, characterized in that the extension (8d, 8e) has a channel height which substantially corresponds to the distance between the pairs of discs (8).

31. Heat exchanger according to one of the preceding claims, characterized in that the disk pairs (10, 11, 12) have a flow cross-section with a channel width b and the housing walls (2c, 2d) at a distance w, where b <w and between the flow cross sections and the housing wall (2c, 2d) material bridges (10a, 1Ob) ₁ in particular formed of lower and / or upper disc, are arranged.

32. Heat exchanger according to one of the preceding claims, character- ized in that the housing (17, 18, 19) is formed at least in two parts and a housing shell (17a, 18a, 19a) and a cover (17b, 18b, 19b).

33. Heat exchanger according to one of the preceding claims, characterized in that the inlet region (27) of the housing

(21) has an inlet nozzle (25) which is arranged in the housing shell (21 a) or in the lid.

34. Heat exchanger according to one of the preceding claims, character- ized in that the outlet region (28) of the housing

(21) has an outlet nozzle (26) which is arranged in the housing shell (21 a) or in the lid.

35. Heat exchanger according to one of the preceding claims, character- ized in that the housing (21) inlet and outlet nozzles (23, 24) for the first fluid.

36. Heat exchanger according to one of the preceding claims, characterized in that the inlet and outlet nozzles (23, 24, 30, 31) are arranged for the first fluid in the lid (21 b) or in the housing shell.

37. Heat exchanger according to one of the preceding claims, character- ized in that the inlet and / or outlet nozzle

(25, 26) longitudinal axes (A), which are inclined relative to the disc pairs (22).

38. Heat exchanger according to one of the preceding claims, characterized in that the heat exchanger has a bypass (56,

57, 58, 59)

39. Heat exchanger according to one of the preceding claims, characterized in that within the housing and parallel to the disc pairs (36, 37, 41, 45) a bypass channel (34, 36, 42, 46) is arranged for the second fluid.

40. Heat exchanger according to one of the preceding claims, characterized in that in the inlet region for the second fluid, a partition wall (38, 39) is arranged.

41. Heat exchanger according to one of the preceding claims, characterized in that a partition wall is arranged in the outlet region for the second fluid.

42. Heat exchanger according to one of the preceding claims, characterized in that the heat exchanger includes at least one check valve, which is preferably integrated in the housing and in the outlet region (26, 32, 53, 58).

43. Heat exchanger according to one of the preceding claims, characterized in that the bypass channel above (36, 46) or below (34, 42) of the disk pairs (37, 45, 36, 41) is arranged.

44. Heat exchanger according to one of the preceding claims, characterized in that the bypass channel as a bypass tube (34, 36, 42, 46) is formed, which is insertable into the housing.

45. Heat exchanger according to one of the preceding claims, characterized in that the bypass channel with respect to the flow channels (3) and / or the passageways is thermally insulated.

46. Heat exchanger according to one of the preceding claims, characterized in that the bypass channel of the flow channels (3) and / or the passageways is arranged substantially at a distance.

47. Heat exchanger according to one of the preceding claims, characterized in that the bypass channel and / or a bypass channel adjacent flow channel (3) and / or passage channel (5) has projections, whereby preferably the flow channels (3) or the passageways (5) from Bypass tube are substantially spaced.

48. Heat exchanger according to one of the preceding claims, characterized in that the bypass channel (34, 36, 42, 46) consists of at least one sub-element, which is preferably designed as an open profile and particularly advantageously as a U-profile or half-pipe.

49. Heat exchanger according to one of the preceding claims, characterized in that the bypass channel (34, 36, 42, 46) consists of two tube halves.

50. Heat exchanger according to one of the preceding claims, characterized in that the bypass channel (34, 36, 42, 46) has at least one longitudinal dividing wall.

51. Heat exchanger according to one of the preceding claims, characterized in that in the inlet or outlet region of the housing, a bypass flap (43) is integrated.

52. Heat exchanger according to one of the preceding claims, characterized in that the inlet region has two separate inlet stubs (47, 48) and a partition wall (49).

53. Heat exchanger according to one of the preceding claims, characterized in that the pairs of discs form a package (51, 51).

60), which can be flowed through by the second fluid in two columns.

54. Heat exchanger according to one of the preceding claims, characterized in that on the one hand of the disk package (51) an inlet chamber (52) and an outlet chamber (53) and on the other hand of the disk package (51) a deflection chamber (54) are arranged for the second fluid ,

55. Heat exchanger according to one of the preceding claims, character- ized in that the bypass is integrated into the housing.

56. Heat exchanger according to one of the preceding claims, characterized in that the bypass is integrated in the lid.

57. Heat exchanger according to one of the preceding claims, characterized in that it comprises at least one flap ..

58. Heat exchanger according to one of the preceding claims, characterized in that the flap is arranged in the inlet region or in the outlet region.

59. Heat exchanger according to one of the preceding claims, characterized in that it comprises at least one bypass valve.

60. Heat exchanger according to one of the preceding claims, characterized in that the bypass valve is integrated in the housing.

61. Heat exchanger according to one of the preceding claims, characterized in that the bypass valve is arranged in the inlet region and / or in the outlet region.

62. Heat exchanger according to one of the preceding claims, character- ized in that the bypass valve is designed as a combination valve.

63. Heat exchanger according to one of the preceding claims, characterized in that the integrated bypass has a pivotable partition wall (59) by means of which the inlet nozzle (57) and the outlet nozzle (58) are short-circuited.

64. Heat exchanger according to one of the preceding claims, characterized in that the first fluid is a liquid coolant, in particular the coolant from the cooling circuit of an internal combustion engine of a motor vehicle and the second fluid recirculated exhaust gas of the internal combustion engine.

65. Heat exchanger according to one of the preceding claims, character- ized in that the first fluid is air and the second fluid recirculated exhaust gas of an internal combustion engine of a motor vehicle.

66. Heat exchanger according to one of the preceding claims, character- ized in that the heat exchanger has an oxidation catalyst (64).

67. Heat exchanger according to one of the preceding claims, characterized in that the disk package (62) of the oxidation catalyst (64) is connected upstream.

68. Heat exchanger according to one of the preceding claims, characterized in that the first fluid is a liquid coolant, in particular the coolant of the cooling circuit of an internal combustion engine of a motor vehicle and the second fluid of the internal combustion engine can be supplied charge air.

69. Heat exchanger according to one of the preceding claims, characterized in that the first fluid is air and the second fluid of an internal combustion engine of a motor vehicle feedable charge air.

70. Use of the heat exchanger according to one of the preceding claims as an exhaust gas cooler in an exhaust gas recirculation system of an internal combustion engine of a motor vehicle or as a heater for interior heating of a motor vehicle.

71. Use of the heat exchanger according to one of the claims preceding claims as a charge air cooler for the direct or indirect cooling of charge air for an internal combustion engine of a motor vehicle.

72. Use of the heat exchanger according to one of the claims preceding claims as an oil cooler for cooling engine oil of an internal combustion engine or transmission oil of a motor vehicle by a liquid coolant, preferably the coolant of the cooling circuit of the internal combustion engine.

73. Use of the heat exchanger in particular according to one of the preceding claims as a refrigerant condenser in the refrigerant circuit of an air conditioning system for motor vehicles.

74. Use of the heat exchanger in particular according to one of the preceding claims as a refrigerant exhaust gas cooler in the refrigerant circuit of an air conditioning system for motor vehicles. Use of the heat exchanger in particular according to one of the preceding claims as a refrigerant evaporator in the refrigerant circuit of an air conditioning system for motor vehicles.