DE102005034137A1 - Heat exchanger for use in motor vehicle, has flow channels flowed through by fluid and designed as disk pairs, where channels comprise longitudinal sides that are connected with housing in firmly bonded manner through soldering or welding - Google Patents

Abstract

The heat exchanger (1) has flow channels (3) flowed through by a fluid, and a housing (2) accommodating the flow channels, where the flow channels are designed as disk pairs. The housing is flowed through by another fluid, which is different from the former fluid. The flow channels have a flat cross-section and longitudinal sides (3a). The disk pairs comprise upper and lower disks that are connected with one another by a rebated joint. The longitudinal sides are connected with the housing in firmly bonded manner through soldering or welding.

Description

The invention relates to a heat exchanger according to the preamble of claim 1 - known by the 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 construction with tube sheets, in which the tube ends are added, is that the tubes are fixed during the soldering process in the tubesheets and thus can not move towards each other during soldering and melting of the solder layer, which is also disadvantageous to the soldering the turbulence inserts with the pipe inner walls. This disadvantage is avoided by systems without tube bottoms, as the following example shows: By the DE 100 60 102 A1 a heat exchanger was known, which is also 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 any 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 the secondary side is flowed through by exhaust gas. In this case, the exhaust gas is relatively straight, that is 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, tube and turbulence plates, is manufactured by "one-piece soldering".

The subject of the application DE 100 60 102 A1 goes according to 9 from a prior art, which relates to a caseless exhaust gas heat exchanger, wherein flat exhaust pipes are formed from discs whose fold has on the longitudinal sides angled erected edge strips which are soldered to adjacent edge strips 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 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 built-in exhaust gas cooler, for. B. the engine compartment of a motor vehicle is not conducive.

It Object of the present invention, a heat exchanger of the aforementioned Kind on the one hand especially solderable, weldable, Klegung right, etc. and on the other hand its outside temperature when using hot, to be cooled Keep media low.

These The 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 integrally connected to the walls of the housing, ie, soldered, welded, glued, etc. 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 minimum soldering gap and proper soldering he be targeted. 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. Thus, crimped disks can prevent, for example, relative movements between the housing and the longitudinally adjacent pair of disks due to different rapid heating of the components and the melting solder layers lead to insufficient soldering of the pair of disks. This also facilitates the tolerance adjustment between 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 is provided in the channel for the second fluid and even up to> 25% when turbulators (for example, embossed in the disc swirling body) 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 intercoolers in many other heat exchanger applications, a sufficient cooling of the housing is often mandatory because otherwise very high thermal stresses at the joints between the housing and disc pairs caused by the large temperature differences and corresponding 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 proposed 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 According to a development of the invention, the flow channels are essentially over their long sides whole length connected to the housing cohesively. In particular, the cohesive connection is performed by soldering, welding, gluing etc., basically is also any other type of connection such as a positive connection or a combination of a cohesive and a positive connection possible.

In a development of the invention, the flow channels are designed as pairs of discs. The pairs of discs form passageways for a second fluid. Between the pairs of discs and the housing exists a connection so that the second fluid has access to the housing and to the housing wall has and so the housing wall and the case for example, cools or heated.

In In a further development of the invention, the flow channels and / or the passageways are substantially taken in their entirety by the housing, so that the Heat transfer between the first and the second fluid substantially completely in the Interior of a housing, which closed with a lid is carried out, wherein 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 he follows.

In a development of the invention is between the lid of a adjacent disc, in particular a lower disc, at least a flow channel a fluid, in particular the first fluid formed, in this way a top disc can be saved and the lid is at the same time also cooled. Because the lid with the housing by material bond, such as soldering, Welding, Gluing, etc., and / or by positive engagement, such as reshaping connected is, there is a heat transfer between lid and housing and vice versa, so that the housing is also cooled.

In another embodiment of the invention is between the bottom portion of the housing or the housing shell and an adjacent disc, in particular the upper disc, and zwi At least one flow channel of the first fluid formed at 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 with a lower disk, in particular a material-locking manner, whereby a disk pair is formed, which materially engages via at least one disk, in particular with the lower disk adjacent to the bottom portion, with the housing shell in the bottom area, in particular by soldering, welding , Gluing, etc. is connected.

In a development of the invention are each a pair of discs forming lower and upper disk by a fold formed at the edge interconnected, thereby the discs are positively, in particular by bending, interconnected. It involves at least one disc, in particular the lower pane, the other pane, in particular the top disc, whereby the discs are hooked into each other, wherein in the stacking direction of the discs and the disc pairs at the same time a tolerance compensation possible is so that during the joining process, as for example soldering, welding, gluing etc., with which the material connection is generated, any openings or column, between the discs can be compensated, so that the joining process process-safe and successful feasible and so a complete cohesive connection between the discs, especially the top and bottom discs, but also between adjacent disk pairs and between adjacent disk pairs Upper and lower washers, done.

In a development of the invention runs an inflow channel and / or at least one outflow channel across the pairs of discs, while the inflow and / or the discharge channel at an angle of 0 ° to 360 ° or -360 ° to the stacking direction the discs and / or the longitudinal direction the discs run through the pairs of discs, especially under one Angle from -50 ° to + 50 ° to the stacking direction, especially advantageous is an angle of 0 ° to Stacking direction, i. outflow and or inflow channel are substantially parallel to the stacking direction. The angles the outflow channel and the inflow channel to the stacking direction and / or the longitudinal direction can thereby be different and assume values between 0 ° and 360 ° or -360 °

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

In a development of the invention, the expression or the cup of a disk pair to an adjacent disk pair, with the discs and the pairs of discs touching and in particular cohesively by soldering, Welding, Gluing etc. are connected. About that In addition, are also a form-fitting Compound and / or a combination of a cohesive and positive Connection possible, as well as other connections.

In a development of the invention is the expression or the cup in the upper disk, in particular by reshaping or prototyping, introduced as well an upper disc ring surface, which a introduced by Ur- or forming sub-disc ring surface of Bottom of a neighboring disc pair touches and in particular cohesively by soldering, Welding, Gluing etc. and / or by positive engagement, such as hooking, connected to the lower disc ring surface is.

In Another embodiment of the invention is another expression, in particular introduced by forming and or original shapes in the lower pane, as well as a lower disc ring surface, which a Oberscheibenringfläche the Upper disk of a neighboring disk pair touches and in particular cohesively by soldering, welding, gluing etc. and / or form-fitting, such as by hooking, is connected to the upper disc ring surface.

In a development of the invention, the flow channels are stacked. Likewise, the Passageways be stacked. In a development, the discs are like that stacked that one slice on an adjacent other slice is stacked and that in particular a top disk on a bottom disk is on top and on the top disc another lower disc is placed on which in turn launched another upper disc is, so that adjacent pairs of discs stacked on each other are. The stack of disks or stacks of disk pairs is in turn in the housing shell inserted, which is closed with a lid. The lid is doing so on the housing put up that he put in the stacking direction on the housing and with this positive fit, in particular by soldering, Welding, Gluing etc. and / or cohesive, in particular by reshaping, hooking, etc., so that during the Joining process, especially soldering, welding or Gluing, a tolerance compensation in the stacking direction of the flow channels or the passageways can be done.

In a further development of the invention the discs of a disc pair disc edge surfaces such that the upper disc of a disc pair has a top disc edge surface and the adjacent bottom disc has a bottom disc surface, the top disc surface corresponds to the bottom disc surface and is materially bonded, in particular by soldering, welding, gluing, etc. 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 disk edge surface and the lower disk edge surface in which the longitudinal side of the disk merges into the disk width in the stacking direction, an impact of the lower and upper disk edge surfaces is formed so that the impact of a disk 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 like two concentric quarter cylinder pushed into each other touch and cohesively, in particular by soldering, welding, gluing, etc. are connected.

In a development of the invention surround the long sides two a flow channel forming pairs of discs at least partially, in particular on the entire pane length like this, that's the case touching Long side the long side an adjacent disc, in particular the other disc of each pair of discs, surrounds and that the two discs on these ways are crimped together.

In a development of the invention encompass the broadsides two forming a flow channel Disc pairs at least partially, especially on the entire Wheel width. The two discs, especially the upper disc and the lower disk of a disk pair, are in this way with each other crimped.

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 DE 102004037391.4, the DE 19718064 B4 as well as the DE 19709601 C2 is hereby expressly disclosed.

In a development of the invention, the characteristics are conical and executed as a truncated cone, from a disc preferably by forming such as punching or generated by prototypes. The smaller of the two diameters having side surface the truncated cone is as a ring surface formed, which the adjacent disc, preferably the lower disc of next Disc pair touched and in particular with this cohesively by soldering, welding, gluing etc. is connected.

In a development of the invention, the characteristics are streamlined, especially with a 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 the DE 19709601 C2 are hereby expressly disclosed in this context.

In a development of the invention are the Falzverbindungen with the housing, especially with the inner surface of the housing, connected, wherein the compound in particular cohesively by Soldering, Welding, Gluing etc. takes place.

In a development of the invention is the inlet region of the housing in Flow direction of second fluid arranged in front of the disc pairs.

In a development of the invention is the exit region of the housing in Flow direction of second fluid behind the disc pairs arranged.

In a development of the invention are the pairs of discs from the second Fluid can flow around substantially parallel to its longitudinal sides.

In a development of the invention, the longitudinal fold is by the same direction angled edges formed by upper and lower disk. The longitudinal fold forms beyond a contact surface for the Casing.

In a development of the invention is the longitudinal fold by opposing angled edges formed by upper and lower disk. The longitudinal fold forms beyond a contact surface for the Casing.

In In a further development of the invention, the pairs of discs have the longitudinal side in the area of the housing walls side channels for the first Fluid on.

The side channels are designed as an extension of the flow cross section of the disk pairs educated. The extension has a channel height, which substantially corresponds to the distance between the pairs of discs.

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

In a development of the invention, the housing is formed at least in two parts, where there is a housing shell and has a lid.

In a development of the invention, the inlet region of the housing an inlet nozzle, which is arranged in the housing shell or in the lid is. About that In addition, the outlet region of the housing has an outlet nozzle on, in the housing shell or is arranged in the lid.

In a development of the invention, the housing has an inlet and outlet nozzle for the first Fluid, wherein the inlet and outlet nozzles for the first fluid in the lid or arranged in the housing shell are and longitudinal axes have, which opposite the disc pairs are inclined.

In In a further development of the invention, the heat exchanger has a bypass. Inside the case and parallel to the disc pairs is a bypass channel for the second Fluid arranged. The mass flow of the second fluid is to, in particular by a partition, branched into at least two partial mass flows, wherein at least a first partial mass flow of the second fluid through the Passageways flows and at least a second partial mass flow of the second fluid through the Bypass flows.

In In a further development of the invention, the pairs of discs form a package, which is double-flowed through by the second fluid. In the entry area for the second Fluid and / or in the outlet area for the second fluid is a Partition arranged. The partition is in particular such rotatably arranged, that an angle, between flow direction the second fluid of a longitudinal side the partition between 0 ° and 360 ° adjustable is.

In According to a development of the invention, the heat exchanger contains at least one non-return valve, which preferably in the housing is integrated and located in the exit area.

In a development of the invention is the bypass channel in the heat exchanger arranged 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 opposite the flow channels ( 3 ) and / or the passageways thermally insulated, in particular such that the heat transfer between the second partial mass flow, which flows through the bypass channel and / or the bypass pipe and the first partial mass flow, which is in particular cooled, is as low as possible.

In a development of the invention, the bypass pipe from the flow channels and / or the Passageways arranged substantially spaced. The spacing is done preferably through into the bypass tube and / or in the flow channels and / or the passageways introduced characteristics or punched out.

In a development of the invention, the bypass pipe consists of at least a sub-element, which preferably as an open profile and especially is advantageously designed as a U-profile or half pipe.

In In a further development of the invention, the bypass pipe comprises two pipe halves, the preferably cohesively by soldering, Welding, Gluing etc. are connected to each other.

In a development of the invention, the bypass pipe at least a longitudinal partition on.

In a development of the invention is in the entry or exit area of the housing at least integrated a bypass flap. The bypass flap is adjustable and can make an angle from 0 ° to Assume 360 °, whereby the mass flow of the second fluid in the first partial mass flow and the second partial mass flow is divided. The first partial mass flow flows through the passageways and is thereby cooled in particular. The second partial mass flow flows, especially uncooled through the bypass. By means of the bypass valve is the first partial mass flow the second fluid through the passageways adjustable and / or controllable and / or adjustable. The second partial mass flow of the second fluid through the Bypass results in dependence from the set first partial mass flow and is therefore also controllable and / or controllable.

In a development of the heat exchanger The entrance area has two separate inlet ports as well a partition on.

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 entry cam mer 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 lid. In particular, the bypass is made in one piece with the lid.

Heat exchanger according to one of the preceding claims, characterized that the flap is arranged in the entry area or in the exit area is.

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

In a development of the invention is the bypass valve as a combination valve executed which hereinafter referred to as Wärmeübertragerventileinrichtung is designated. The heat transfer valve device is characterized in that the valve disc between a first open position, in which the bypass outlet is closed and the heat exchanger outlet open is, and a second opening position is rotatable, in which the bypass outlet is opened and the heat exchanger outlet closed is. Due to the rotatable valve disc can also at high pressures a sufficient tightness guaranteed become.

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

One Another preferred embodiment the heat exchanger valve device is characterized in that one of the fluid passage openings in the fixed valve disc with the heat exchanger output and the other fluid passage opening with communicates with the bypass output. Depending on the coverage the fluid passage openings in the valve discs more or less or no fluid passes to the bypass outlet or the heat exchanger outlet.

One Another preferred embodiment the heat exchanger valve device is characterized in that the fixed valve disc has a recess in which the rotatable valve disc is guided. This provides the advantage that on a valve disc guide the valve housing can be waived.

One Another preferred embodiment the heat exchanger valve device is characterized in that the fixed valve disc an external thread has, with the fixed valve disc in a complementary trained Internal thread of the valve housing is screwed. This will cause the mounting of the fixed valve disc simplified.

One Another preferred embodiment the heat exchanger valve device is characterized in that of the rotatable valve disc an actuator rod goes out. By the actuator rod, preferably from the valve body led out is, is the actuation the rotatable valve disc simplified.

One Another preferred embodiment the heat exchanger valve device is characterized in that the valve discs at least partially are made of ceramic. Instead of ceramics can also be stainless steel be used.

One preferred embodiment 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 output open is, and a second extreme position is movable back and forth, in which the bypass outlet is opened and the heat exchanger output closed is. Through the valve spool can even at high pressures a sufficient tightness guaranteed become.

One Another preferred embodiment the heat exchanger valve device is characterized in that the valve slide partially off Ceramic is formed. Stainless steel can also be used instead of ceramics become.

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

One Another preferred embodiment the heat exchanger valve device is characterized in that the valve slide with a sealing element for the Entrance is equipped. Preferably, the input is with a Sealing seat for the Equipped sealing element.

One Another preferred embodiment the heat exchanger valve device is characterized in that the sealing element is an input facing sealing surface having the shape of a spherical section. By using a ball section with a large diameter will shift the valve spool easier.

One Another preferred embodiment the heat exchanger valve device is characterized in that the sealing element on the valve spool guided back and forth is. This will make the closure the entrance with the sealing element, which also serves as a closing element is simplified.

One Another preferred embodiment the heat exchanger valve device is characterized in that the sealing element by a spring device is biased against the entrance. This will close the entrance tightly allows.

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

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

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

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

In In a further development of the invention, the disk package is an oxidation catalyst upstream, as described in the unpublished DE 102005014295.8 is disclosed. The entire contents of unpublished DE 102005014295.8 is hereby expressly disclosed.

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

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

In a development of the invention is the heat exchanger as exhaust gas cooler in an exhaust gas recirculation system an internal combustion engine of a motor vehicle or as a heater for interior heating used of a motor vehicle, while that of the second Fluid transferred to the first fluid Heat to it used to heat the passenger compartment of a vehicle.

In a development of the invention, the heat exchanger as oil cooler for cooling of engine oil an internal combustion engine or transmission oil of a motor vehicle a liquid Coolant, preferably the coolant the cooling circuit the internal combustion engine used.

In a development of the invention is the heat exchanger as a refrigerant condenser in the refrigerant circuit an air conditioner for Used motor vehicles.

In a development of the invention is the heat exchanger as a refrigerant gas cooler in the refrigerant circuit an air conditioner for Used motor vehicles.

In a development of the invention is the heat exchanger as a refrigerant evaporator in the refrigerant circuit an air conditioner for Used 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 are formed circumferentially and continuously so that they have a planar contact with each other ( 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 panes may, for example, abut surface-to-edge at their contact line, so that, in a section perpendicular to the line of contact, the two panes largely pass over a certain distance run parallel to each other. One or both discs may be formed in the area of the investment line, for example, also spherically against each other, so that in the section perpendicular to the contact line touching a straight line with a circle segment or, if both are performed crowned, the punctiform Berüh tion of two circle segments results in only one Touch point but no contact line. 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 designed very flexible according to the invention, because is sealed by the housing of the flow channel for the 2nd fluid on the long sides everywhere and therefore no soldering with adjacent disc edges is required at the outer edges of the disc pair. 2c represents a good compromise between process-optimized design of the disc pair, which allows a circumferential areal 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.

To a further advantageous embodiment of the invention is casing formed at least in two parts, d. H. for example, from one first trough-shaped Housing part, a housing shell, and a second lid-shaped Part, a lid, trained. Both parts can be put together and simply joined together, especially soldered, welded, glued etc. become. With such a housing concept is also an optimal Joining process, in particular soldering process, welding process, Gluing process, etc., which reaches stacked pairs of discs when the housing parts also in the stacking direction of the disk pairs plugged into each other or one above the other be plugged and by soldering, Welding, Gluing etc. while of the joining process, especially the soldering process, Welding process, Gluing process, etc., to the housing together become. With suitable design can then also the housing parts to the same extent move the pairs of discs aufeinender, so that, for example no fissures, soldering, welding and / or soldering through the melting solder layers Small defects arise. Advantageously, the housing shell as well as the lid as forming and / or molded parts such as Deep-drawn parts are manufactured, wherein the Gehäusescha le also the entrance and exit area for can form the second fluid. Furthermore, on the housing, be it's the case shell or the housing cover, Inlet and outlet ports for both the first and the second Fluid are formed, for. B. as passages. The location and shape of the neck can be chosen according to the requirements of the heat exchanger. So can for the second fluid of the inlet and outlet nozzles at the same radiator end or at opposite Ends lie (see explanations this below) and the entry and exit can be in any in any direction, e.g. in the longitudinal direction of the radiator, after above - here from the lid, down from the case or sideways out of the case.

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 valves 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, which separates the inlet region into two regions, one for the bypass fluid flow and the other for the heat exchanger fluid flow, can be provided in the inlet region for the second fluid. Separating elements can be clamped, welded or soldered, for example, in 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 inlet opening, of course, a separation of the fluid flows in the supply of the second fluid is 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- on 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 valve can also be integrated in the inlet region of the second fluid so that the gas flow according to the requirements directly into the bypass channel or in the Heat exchanger channels is directed. Even with such an integrated bypass flap can still be required between the beginning of the bypass and the flap for sealing an additional separator. 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).

Of the inventive heat exchanger can be very different versions to the bypass channel. In a further development of the invention the bypass in the stacking direction of the disk pairs below the bottom Disc or inserted above the top disc. He borders directly to the housing at. In a further development of the invention, the bypass is laterally placed next to the stacked disc pairs in the housing. In a further education the invention, the bypass channel is made integral with the housing by one or more longitudinal beads so in the case imprinted be that thereby the bypass channel is formed, which on one side of the housing wall and bounded on the other side by the first disc of the disc bundle is. In one embodiment of the invention, a bypass is such formed, that a substantially U-shaped shell on a housing side attached and in particular with this is joined and in particular with this soldered, welded, glued, etc is. In this case, the bypass is between attached shell and the housing wall locked in. Furthermore, a heat exchanger according to the invention can also be equipped with a completely external one Bypass be combined, so a closed flow channel for the 2. fluid, with the heat exchanger may be connected, for example, welded, soldered, or with the heat exchanger can be fixed in common holders. An external bypass can but also completely separately from the heat exchanger guided become.

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

In a development of the invention, which form the channel Structures in the longitudinal direction over the through the stacked discs formed heat exchanger channels in the Entry and / or exit area of the second fluid into it. In this way, a separating element between bypass fluid flow and heat exchange fluid flow omitted. In one embodiment of the invention is the integrated Bypass flap designed such that no additional Separating element for the bypass channel is required.

Of the Bypass duct is said to pass the second fluid past the heat exchanger ducts without allow strong energy transfer from or to the first fluid and he should therefore as possible be thermally decoupled from the first fluid. The decoupling For example, by a knob or bead support of the bypass channel against the housing wall and / or against the disk stack. The knobs or beads can in this case both from a structure forming the bypass channel, for example a pipe and / or from the housing wall or the adjacent first disc of the disc stack. As an insulating element can also be an additional insulation between the bypass channel and adjacent structures, which has a low thermal conductivity (good insulation) has. The insulation is done by insulating materials and / or by the shaping, in particular through a ribbed structure.

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

In A further embodiment of the invention provides that the heat exchanger two or can be flowed through with multiple flooding is, d. H. the second fluid is divided into sub-streams, each through a part of the heat exchanger channels in parallel or conducted in countercurrent become. For separation of the partial flows can the same arrangements of dividers and inlet / outlet openings be used, as with the integration of the bypass tube described.

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 Er increase in exhaust gas recirculation rate and fuel efficiency can be used if backflow into the other tide 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 are mehrflutige heat exchanger formed with min a deflection of the second fluid. It will the second fluid is not divided into sub-streams but by a part of the fluid channels of Entrance end of the second fluid led to the other end where it deflected, in particular substantially deflected by 180 °, and by a other part of the fluid channels is returned again. The deflection can be done in several sub-stages. But it can also be provided several deflections, wherein the exit of the second fluid with an odd number of deflections at the entrance end of the heat exchanger takes place and the exit at an even number of diversions at the other end of the heat exchanger he follows.

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

In a development of the invention is the heat exchanger as a charge air intercooler between formed the compressor stages of a turbo engine, wherein in the deflection in particular, no separating elements or other deflecting elements formed are, since the deflection is done by a closed at this end housing.

In a development of the invention is in the U-flow training no separate bypass tube is required as in bypass mode the Connection between inlet and outlet nozzles in the combined inlet / outlet area the radiator shorted. In the case of cooled Exhaust gas recirculation is the path between the inlet and outlet connection blocks and the second fluid, in particular the exhaust gas is passed through the heat exchanger channels.

In a development of the invention of the heat exchanger with U-flow with an internal bypass flap and / or a combination valve and / or with an external bypass flap and / or with a combination valve. at an external bypass valve in combination with a U-flow cooler is the To provide division of the inlet / outlet area by a separating element and the bypass flap is then integrated in particular in a module, which can short circuit the way through the exhaust gas cooler directly.

As mentioned, can the heat exchanger according to the invention particularly advantageous as an exhaust gas cooler be used; in particular, the cooling of the housing shell is beneficial because the coolant partially in direct contact with the housing wall or indirectly via material bridges with the housing wall communicates. The cooling of the exhaust gas cooler Depending on the application at a high or low pressure exhaust gas recirculation (exhaust gas extraction before or after the exhaust gas turbine) by the coolant of the cooling circuit the internal combustion engine or by air, with an adjustment the flow cross sections and the heat transfer, z. B. is done by turbulence inserts. Advantageous in use is as exhaust gas cooler also the arrangement of an oxidation catalyst in the flow direction the exhaust gas in front of the disc 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 area the radiator, because then the flap / combi valve is protected from contamination.

Of the Heat exchanger according to the invention can also advantageous as intercooler, be it with direct cooling (Air) or with indirect cooling (liquid coolant), be used. Furthermore, the heat exchanger according to the invention can be used advantageously as a coolant-cooled oil cooler or as air cooled Condenser of an automotive air conditioning system can be used. at the different uses is just an adaptation to the different media and heat transfer conditions 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 performed in parallel to the exhaust gas, which effectively serves to prevent boiling, and be guided in the outlet region of the exhaust gas, the coolant flow in countercurrent to the exhaust gas, whereby a particularly efficient heat transfer in the rear part of the heat exchanger is achieved , please refer DE 10328746 whose content 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, to draw two circuits for the first medium arranged on the other and be flowed through 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 the first fluid in countercurrent to the second fluid are particularly useful if the first and second medium have similar heat capacities or the second medium a higher one Heat capacity than that first, especially if both media are gaseous.

embodiments The invention are illustrated in the drawing and are explained in more detail below. It demonstrate

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

2a . 2 B . 2c Further embodiments for the formation of the coolant 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,

4 an exploded view of the exhaust gas cooler with housing shell, disc pairs and cover,

5a an exploded view of the pairs of discs and the lid,

5b an exploded view of an unfastened pair of disks, which comprises at least one upper disk and at least one lower disk, and a further lower disk of an adjacent disk pair

5c a section CC by an exploded view of an unfastened disc pair, which comprises at least one upper disc and at least one lower disc

5d a perspective view of a joined pair of discs

5e a view of an assembled pair of discs in the flow direction of the second fluid

6a . 6b . 6c Embodiments of a two-part housing of the exhaust gas cooler,

7a . 7b Longitudinal sections through the exhaust gas cooler with different exhaust gas and coolant guidance,

8a . 8b Longitudinal sections through the exhaust gas cooler with integrated bypass pipe and dividing wall in the inlet or outlet area,

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

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

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

12 a longitudinal section through an exhaust gas cooler with double-flow and integrated bypass with bypass flap,

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

14 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

15 a longitudinal section DD through two verkrimpte and joined pairs of discs and

16 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.

1 shows a heat exchanger according to the invention 1 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 before or after an exhaust gas turbine (high pressure or low pressure feedback) and cooled one or two stages supplied to the intake of the engine again. The amount of gas taken off is regulated via an exhaust gas recirculation valve (EGR valve). The illustrated exhaust gas cooler 1 Is exhaust gas flows through 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 on, which consists of a trough-shaped housing shell 2a and a lid 2 B exists - both parts are preferably formed as sheet metal parts and can be made by deep drawing. In the housing shell 2a is a package of disk pairs 3 arranged, which are flowed through by the coolant. The pairs of discs 3 extend over the full width of the housing shell 2a , Which two in the drawing vertically shown and parallel to each other housing walls 2c . 2d having. The pairs of discs 3 have long sides 3a on, which on the housing walls 2c . 2d abut, and form flow channels, which with turbulence inserts 4 are equipped to increase the heat transfer. The pairs of discs 3 are arranged in parallel spaced apart and form passageways 5 for the exhaust. In the passageways 5 are to increase the heat transfer turbulence inserts 6 arranged. All parts of the exhaust gas cooler 1 are cohesive, ie connected by soldering. The soldering is preferably carried out in one operation in a soldering furnace, not shown. The pairs of discs each have a top disc 80b and a lower pane 80c on.

2a shows a further embodiment of the invention as a detail of an exhaust gas cooler - for the same parts are the same reference numerals as in 1 used. Between the two housing walls 2c . 2d are two modified pairs of discs 7 arranged, which with their long sides 7a by soldering to the housing walls 2c . 2d are connected. The pairs of discs 7 each consist of a top disk 7b and a lower disk 7c , which are connected 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 causes a cooling of the housing walls, which are heated by the exhaust gas stream.

2 B shows a further embodiment of the invention for the formation of a pair of discs 8th , which consists of a top disk 8a . 80b and a lower disk 8b . 80c put together and laterally by a fold 8c closed is. The flow cross section of the disc pair 8th is laterally to side channels 8d . 8e extended, which is about the height of the exhaust ducts 5 or in the exhaust ducts 5 arranged turbulence inserts 6 exhibit. The side channels 8d . 8e , which are flowed through by the coolant, thus extending from a pair of discs 8th to the adjacent pair of discs and are the entire surface of the housing walls 2c . 2d at. This results in a very good cooling of the housing walls 2c . 2d achieved, which are thus isolated from the exhaust stream. Identical features are provided with the same reference numerals as in the preceding figures.

2c shows a further formation of pairs of discs 9 which is a top disk 80b and a lower pane 80c includes, between housing walls 2c . 2d , Wherein by an extension of the flow cross-section side channels 9a . 9b are formed, which, however, do not have the full height of the exhaust ducts, but only a part, for. B. 50% - the remaining channel height is in each case by a longitudinal fold 9c . 9d bridged. This design also provides a very good cooling of the housing walls 2c . 2d because they are lapped by coolant. Identical features are provided with the same reference numerals as in the preceding figures.

The 3a . 3b . 3c show further embodiments of the invention for embodiments of disc pairs 10 . 11 . 12 , each from a top disk 80b and a lower disk 80c are formed, whose flow channels have a width b, which is smaller than the clear width w of the housing - between the flow channels of the disc 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. This also provides a good cooling effect, ie an indirect cooling of the housing walls 2c . 2d achieved, ie by heat conduction through 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 items of an exhaust gas cooler, which according to the embodiment according to 1 equivalent. Identical features are provided with the same reference numerals as in the preceding figures. In the drawing below is a trough-shaped housing shell 13 shown, which frontally, ie on its narrow side an exhaust gas inlet opening 13a and on the opposite narrow side (largely obscured) an exhaust gas outlet opening 13b having. Above the housing shell 13 are three pairs of discs 14 , a cover plate 15 and the housing cover 16 shown. The approximately rectangular shaped pairs of discs 14 have at their long sides each angled edge strips 14a on, which are formed as folds and with the inside of the housing shell 13 are solderable. The pairs of discs 14 are flowed through by coolant and therefore have cup-like characteristics 14b . 14c on, which in the soldered state each form a feed and a discharge channel for the disk pairs, which are thus flowed through parallel to each other. The coolant connections (not shown here) are located in the cover 16 of the housing. It can also be seen from this illustration that the individual parts of the exhaust gas cooler can be easily assembled and prepared for the soldering process.

5a shows a further illustration of the pairs of discs 14 according to 4 in a frontal view, ie seen in the flow direction of the exhaust gas. It will be the same reference numbers as in 4 used. The pairs of discs 14 are arranged parallel and at a distance from each other and form approximately rectangular flow channels (passage channels) 17 for the exhaust gas, here turbulence inserts, as in the 1 to 3 are shown omitted. The pairs of discs 14 each consist of two discs, namely a top disc 14d and a lower disk 14e , which in each case on their longitudinal sides by the angled fold 14a connected to each other. The front ends 14f , which form the leading edges for the exhaust gas, however, are interconnected by a shallow fold. Thus, the pairs of discs are 14 peripherally sealed circumferentially. The cup-like characteristics 14b are from the top disk 14d formed and lie on the adjacent lower disc 14e Thus - a transverse to the exhaust gas flow direction extending inflow or outflow channel for the coolant ge create. The characteristics are aerodynamically designed to achieve a low exhaust gas pressure drop, z. B. - like out 4 visible - 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.

5b shows an exploded view of an unfused pair of discs 3 . 14 which has at least one upper disk 80b and at least one lower pane 80c includes, as well as another lower pane 80c a neighboring disc pair. Identical features are provided with the same reference numerals as in the preceding figures. The upper disc 80b and the lower disk 80c each have a disc opening 81 on, which is designed as a bore. The upper disc 80b includes at least one expression 14b , in particular two forms 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 . 82c , which are parallel to the disk surface 92 the top disk 80b and the lower disk 80c and perpendicular to the stacking direction of the disk pairs 3 . 14 is arranged. The lower pane 80c has a lower disc ring surface 83 . 83c on which integral with the disk surface 92 is formed and in the area of the disc opening is identical to this. In the joined, in particular soldered, welded, glued, etc., state, the upper disc ring surface touch 82 . 82c a pair of discs 3 . 14 and the lower disc ring surface 83 . 83c a neighboring disc pair 3 . 14 and are connected to each other cohesively. The upper disc 80b includes at the disc edges a top disc edge surface 85 , The lower pane 80c includes at the disc edges a lower disc edge surface 86 , Upper plate rim surface 85 and bottom plate surface 86 correspond to each other and are cohesively, in particular by soldering, welding, gluing, etc. interconnected. The top edge surface 85 runs in the longitudinal direction of the disc substantially parallel to the signature edge surface 86 , as well as the top edge surface 85 in the direction of the disk width which, in particular, is oriented substantially perpendicular to the longitudinal direction of the disk and substantially perpendicular to the stacking direction of the disks, substantially parallel to the bottom disk surface. In the sections of the upper edge surface and the lower edge surface, in which the longitudinal side of the disc merges in the stacking direction in the disc width, is a shock 93 the bottom and top edge surface formed such that the shock 93 a disk edge surface is formed in the longitudinal direction substantially as a quarter cylinder and that touch the quarter cylinder of the lower and upper disk substantially like two telescoped concentric quarter cylinder and are materially connected, in particular by soldering, welding, gluing, etc.

5c shows a section CC through the exploded view 5b an unfused pair of discs, which at least one upper disc 80b and at least one lower pane 80c includes. Identical features are provided with the same reference numerals as in the preceding figures.

5d shows a perspective view of a joined pair of discs 3 . 14 , Identical features are provided with the same reference numerals as in the preceding figures. In the joined, in particular soldered, welded, glued, etc., state, the upper disc ring surface touch 82 . 82c a pair of discs 3 . 14 and the lower disc ring surface 83 . 83c a neighboring disc pair 3 . 14 and are connected to each other cohesively. The upper disc 80b includes at the disc edges a top disc edge surface 85 , The lower pane 80c includes at the disc edges a lower disc edge surface 86 , Upper plate rim surface 85 and bottom plate surface 86 correspond to each other and are cohesively, in particular by soldering, welding, gluing, etc. interconnected. The top edge surface 85 runs in the longitudinal direction of the disc substantially parallel to the signature edge surface 86 , as well as the top edge surface 85 in the direction of the disk width which, in particular, is oriented substantially perpendicular to the longitudinal direction of the disk and substantially perpendicular to the stacking direction of the disks, substantially parallel to the bottom disk surface. In the sections of the top edge surface and the bottom edge surface, in which the longitudinal side of the disc in the stacking direction into the slices wide is a push 93 the bottom and top edge surface formed such that the shock 93 a disk edge surface is formed in the longitudinal direction substantially as a quarter cylinder and that touch the quarter cylinder of the lower and upper disk substantially like two telescoped concentric quarter cylinder and are materially connected, in particular by soldering, welding, gluing, etc.

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

6a . 6b . 6c show different shapes for the formation of housings 17 . 18 . 19 , each box-shaped or trough-shaped housing shells 17a . 18a . 19a exhibit. Identical features are provided with the same reference numerals as in the preceding figures. Different are the lid shapes 17b . 18b . 19b , The lid 17b has a circumferential bead (gutter) 17c on, which on the circumferential upper edge of the housing shell 17a can be placed and thus soldered. The lid 18b has an upstanding peripheral edge 18c on, which on the inner wall of the housing shell 18a is applied. The lid 18b Thus, during soldering (during melting of the solder layers of the disk package) "sag." The lid 19b has an angled edge 19c on which the upper edge of the housing shell 19a engages around the outside and thus can be soldered all around. All parts shown are inexpensive to produce as deep-drawn parts.

7a shows an exhaust gas cooler 20 in longitudinal section with a housing 21 , consisting of housing shell 21a , Lid 21b , an inlet of the first fluid 90 and an exit of the first fluid 91 , In the case 21 is a package 22 (hatched shown), consisting of the aforementioned, 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 relevant coolant connections are as nozzles 23 . 24 in the lid 21b of the housing 21 arranged. The exhaust gas, represented by arrows A, zen passes through an inlet 25 in the exhaust gas cooler 20 and leaves him via an outlet 26 , In the exhaust gas flow direction in front of the disk pack 22 is an entry area 27 which acts as a diffuser and downstream of the disk pack 22 is an exit area 28 in the case 21 leave which in the outlet nozzle 26 passes. The exhaust gas, represented by the arrows A, thus flows substantially in the longitudinal direction ("axially") through the exhaust gas cooler 20 or the disc package 22 ,

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, can be reached. 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 the 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.

8a and 8b show further embodiments of the invention, namely an exhaust gas cooler 33 with bottom bypass channel 34 and an exhaust gas cooler 35 with overhead bypass channel 36 , Identical features are provided with the same reference numerals as in the preceding figures. Both bypass channels 34 . 36 may be formed as a tube and be inserted into the housing, in each case parallel to the hatch packages shown hatched 37a . 37b , The exhaust gas cooler 33 according to 8a has a separating or sealing element in the exhaust gas inlet region 38 on, which is the separation of the exhaust gas stream into two partial streams for the disk package 37a on the one hand and the bypass tube 34 on the other hand serves. The exhaust gas cooler 35 according to 8b has an exhaust gas supply with 90 degrees deflection from the lid side on - the corresponding is an angled separating element 39 arranged in the exhaust gas inlet region, which seals the exhaust gas streams against each other. In both cases, an unillustrated bypass valve is thus arranged outside of the exhaust gas cooler.

9 shows as a further embodiment of the invention, an exhaust gas cooler 40 with disc package 41 and a bypass channel disposed thereunder 42 , wherein in the exhaust gas inlet region, represented by the exhaust gas arrow A, a pivotable bypass flap 43 is arranged. Identical features are provided with the same reference numerals as in the preceding figures. This allows the exhaust gas flow either through the disc package 41 or through the bypass channel 42 be steered, with intermediate positions are possible. The design of a bypass flap is known from the prior art, also under the term exhaust manifold.

10 shows as a further embodiment of the invention, an exhaust gas cooler 44 with a disc package 45 (Heat exchanger part) and a bypass channel arranged on top 46 , each with separate exhaust gas inlets 47 . 48 in the case of the Ab gas cooler 44 assigned. Identical features are provided with the same reference numerals as in the preceding figures. Between the two exhaust gas inlets 47 . 48 is a partition or partition 49 arranged, which may be soldered to the housing.

11 shows as a further embodiment of the invention, a double-flow exhaust gas cooler 50 with a disc package 51 (Heat exchanger part), an exhaust gas inlet chamber 52 , a partitioned by a partition exhaust gas outlet chamber 53 and a deflection chamber 54 for the exhaust gas flow, represented by an elongated, U-shaped arrow A. The same features are provided with the same reference numerals as in the preceding figures.

12 shows a further embodiment of the invention, namely a double-flow exhaust gas cooler 55 which is an exhaust gas chamber 56 with an exhaust gas inlet nozzle 57 and an exhaust outlet 58 having. Identical features are provided with the same reference numerals as in the preceding figures. In the exhaust chamber 56 is a swiveling exhaust flap 59 (solid line) arranged, which in a dashed line position 59 ' is pivotable. In the position 59 are inlet nozzles 57 and outlet nozzle 58 separated from each other, ie from the gas stream flows through the heat exchanger part 60 corresponding to the U-shaped arrow A and enters through the exhaust pipe 58 out; the entire exhaust stream is thus cooled. In the event that no exhaust gas cooling is needed, the exhaust flap 59 in the dashed line position 59 ' adjusted, so that in the inlet pipe 57 entering exhaust gas flow directly - in short - in the outlet nozzle 58 is steered and out of the exhaust gas cooler 55 exit. The exhaust gas chamber 56 thus forms a bypass channel, represented by a dashed arrow B. The disk package 60 is thus bypassable in the bypass. The exhaust gas cooler 55 So has an integrated bypass with integrated bypass flap.

13 shows as a further embodiment of the invention, an exhaust gas cooler 61 with a heat exchanger part 62 (Disc package), which one-flow ("axial") can be flowed through by exhaust gas, according to the exhaust arrows A. The same features are provided with the same reference numerals as in the preceding figures The exhaust gas cooler 61 has a designed as a diffuser exhaust inlet region 63 in which an oxidation catalyst 64 is arranged, which - as known from the prior art - the exhaust gas purification is used. An advantage of this arrangement, in addition to the space-saving design, that by the exhaust ducts, not shown, of the oxidation catalyst, a rectification of the exhaust gas flow and thus an improved loading of the downstream disk pack 62 can be achieved.

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. In the inlet region of the second fluid in the heat exchanger, a first flood occur 87 of the second fluid, which is designed in particular as a bypass, and a second flood 88 of the second fluid. The first flood 87 and the second flood 88 are by a partition wall-shaped sealing element 89 separated from each other sealing. The sealing element 89 is aerodynamically designed for the second fluid such that the entering obliquely to the disc longitudinal direction in the heat exchanger floods through the element provided with a radius Abdichtele be transferred to the entry into the disc pack in the disc longitudinal direction. 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 integrated for the second tide and designed such that the first check valve 94 a first pivot 98 adjacent to the housing bottom, which includes a pivoting movement of a first valve flap 96 about 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 includes 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.

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 top discs 80b and the lower washers 80c are arranged substantially parallel spaced from each other, wherein the distance between a top plate 80b and a lower disk 80c a pair of discs 3 . 14 the height of the flow channel for the first fluid and the distance between a lower disc 83 and the top disk 82 of an adjacent disk pair forms the height of the passageway for the second fluid. The lower washers 81c are with an opening 81 formed around the concentric a lower disc ring surface 83 is trained. The top discs 81b also have an opening 81 , In the area of these openings are conical shapes 14b perpendicular to the disc surface and in stacking disc direction of the upper discs conical. In the section of shaping 14b of the smaller of the two cone diameters, which are located at the two cone ends, kinks the expression and runs parallel to the disc surface, creating a Oberscheibenringfläche 82 is formed, which the lower disc ring surface 83 touches an adjacent pair of discs and cohesively, in particular by soldering, welding, gluing, etc. is connected to this. The Oberscheibenknicken beyond the characteristics 14b in the direction of the inlet region for the second fluid in the direction of the housing bottom. The height of the flow channel decreases until the top disc 80b and the lower disk 80c a pair of discs touch and parallel to each other and cohesively, in particular by soldering, welding, gluing, etc. are interconnected. The lower pane 80c is in the longitudinal direction slightly over the length of the upper disc 80b addition, creating a final width range 101 the lower pane 80c arises, which around the associated upper disk 80b of the disc pair 3 . 14 , at least in sections over the entire width of the disc, is bent and thus engages around the upper disc, which is referred to as 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 discs are crimped with the upper discs at least in sections over the entire width of the disc on the exit side of the disc package, but not in 15 is shown. The Verkrimpung takes place at least in sections on the two long sides of the discs, which also not in 15 is shown. In a further embodiment, not shown, the upper disk can engage around the lower disk.

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 through a sealing element 89 , which is formed as a wall, separated from each other sealingly. 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 Features of the various embodiments can be combined with each other. The invention is also for others can be used as the areas shown.

Claims (75)

Heat exchanger with flow channels, which are 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 ) cohesively, in particular by soldering, welding, gluing, etc. with the housing ( 2 ) are connected. Heat exchanger according to claim 1, characterized in that the flow channels ( 3 ) over the long sides ( 3a ) are materially connected to the housing substantially over its entire length, in particular by soldering, welding, gluing, etc. Heat exchanger according to claim 1 or 2, characterized in that the flow channels as pairs of discs ( 3 . 7 . 8th . 9 . 10 . 11 . 12 . 14 ) and in connection with the housing ( 2 ) Passageways ( 5 ) for the second fluid. Heat exchanger according to one of the preceding claims, characterized in that the flow channels ( 3 ) and the passageways ( 5 ) substantially in their entirety through the housing ( 2 ). Heat exchanger according to one of the preceding claims, characterized in that between a cover ( 2 B . 16 . 17b . 18b . 19b ) and a lower pane adjacent to the lid ( 7c . 80c ) at least one flow channel ( 3 ) is formed for the first fluid. Heat exchanger according to one of the preceding claims, characterized in that between a to a bottom portion of a housing shell ( 2a . 13 ) adjacent upper disk ( 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. Heat exchanger according to one of the preceding claims, characterized in that the pairs of discs ( 3 . 7 . 8th . 9 . 10 . 11 . 12 . 14 ) a lower and a lower disk ( 7b . 7c . 14d . 14e . 80b . 80c ), which at the edge by a fold ( 3a . 7a . 8c . 14a ) are interconnected. Heat exchanger according to one of the preceding claims, characterized in that at least one inflow channel and / or at least one outflow channel across the pairs of discs ( 14 ) runs. Heat exchanger according to one of the preceding claims, characterized in that the pairs of discs ( 14 ) at least one cup or at least one expression ( 14b ) exhibit. Heat exchanger according to one of the preceding claims, characterized in that the expression ( 14b ) of a disk pair ( 14 ) extends to an adjacent pair of disks, this touches and in particular with the adjacent pair of disks cohesively by soldering, welding, gluing, etc. is connected. Heat exchanger according to one of the preceding claims, characterized in that the expression ( 14b ) in the upper disk ( 80b ) and the expression ( 14b ) a Oberscheibenringfläche ( 82 ), which has a lower disc ring surface ( 83 ) of the lower pane ( 80c ) of an adjacent disk pair touched and in particular cohesively by soldering, welding, gluing, etc. is connected to the lower disk ring surface. Heat exchanger according to one of the preceding claims, characterized in that an expression in the lower disc ( 80c ) is introduced and the expression a lower disc ring surface ( 83c ), which has a disc surface ( 82c ) of the upper disk ( 80b ) of an adjacent disk pair touches and in particular cohesively by soldering, welding, gluing, etc. with the Oberscheibenringfläche ( 82c ) connected is. Heat exchanger according to one of the preceding claims, characterized in that the flow channels ( 3 ) are stacked. Heat exchanger according to one of the preceding claims, characterized in that the cover ( 2 B . 16 . 17b . 18b . 19b ) in the stacking direction on the housing ( 2 ) or the housing shells ( 2a . 13 . 17a . 18a . 19a ) is attached. Heat exchanger according to one of the preceding claims, characterized in that the upper disc ( 80b ) of a disk pair ( 14 ) a top edge surface ( 85 ) and the associated lower pane ( 80c ) a bottom plate surface ( 86 ), wherein the outer disc edge surface ( 85 ) with the lower disk edge surface ( 86 ) Corresponds and cohesively, in particular by soldering, welding, gluing, etc. is connected. Heat exchanger according to one of the preceding claims, characterized in that longitudinal sides ( 3a ) of two a flow channel ( 3 ) forming pairs of discs ( 14 ) at least be areal manner, in particular on the entire disc length, engage around and in particular that the housing contacting the longitudinal side ( 3a ) the long side ( 3a ) of an adjacent disc, in particular of the other disc of the respective disc pair, surrounds. Heat exchanger according to one of the preceding claims, characterized in that broad sides of two a flow channel ( 3 ) forming pairs of discs ( 14 ) at least partially, especially on the entire width of the disc, embrace. Heat exchanger according to one of the preceding claims, characterized in that the pairs of discs ( 14 ) turbulence generating devices ( 4 ), in particular turbulence inserts or embossed structural elements, which in the flow channels ( 3 ) are arranged. Heat exchanger according to one of the preceding claims, characterized in that the characteristics ( 14b . 84 ) are conical. Heat exchanger according to one of the preceding claims, characterized in that the characteristics ( 14b . 84 ) in the direction of the long sides ( 14a ) are streamlined, in particular formed with an elongated or elliptical cross-section. Heat exchanger according to one of the preceding claims, characterized in that between flow channels or in the passageways ( 5 ) turbulence generating devices ( 6 ), in particular turbulence inserts or from the disk pairs ( 3 . 7 . 8th . 9 . 10 . 11 . 12 ) formed structural elements are arranged. 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 ) with the housing ( 2 . 2c . 2d ) are connected. 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 disk pairs ( 22 ) is arranged. Heat exchanger according to one of the preceding claims, characterized in that the exit region ( 28 ) of the housing ( 21 ) in the flow direction of the second fluid (A) behind the disc pairs ( 22 ) is arranged. Heat exchanger according to one of the preceding claims, characterized in that the pairs of discs ( 3 . 7 . 8th . 9 . 10 . 11 . 12 . 14 ) of the second fluid substantially parallel to their longitudinal sides ( 3a . 7a . 14a ) are flowed around. 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 ). Heat exchanger according to one of the preceding claims, characterized in that the longitudinal fold ( 7a ) by oppositely angled edges of upper and lower disc ( 7b . 7c ) is formed and a contact surface for the housing ( 2c . 2d ). Heat exchanger according to one of the preceding claims, characterized in that the pairs of discs ( 8th . 9 ) along the housing walls ( 2c . 2d ) Side channels ( 8d . 8e . 9a . 9b ) for the first fluid. Heat exchanger according to claim 28, characterized in that the side channels ( 8d . 8e . 9a . 9b ) as an extension of the flow cross-section of the disk pairs ( 8th . 9 ) are formed. Heat exchanger according to claim 29, characterized in that the extension ( 8d . 8e ) has a channel height substantially equal to the spacing of the pairs of discs ( 8th ) corresponds. Heat exchanger according to one of the preceding claims, characterized in that the pairs of discs ( 10 . 11 . 12 ) has a flow cross-section with a channel width b and the housing walls ( 2c . 2d ) have a distance w, where b <w and between the flow cross-sections and the housing wall ( 2c . 2d ) Material bridges ( 10a . 10b ), in particular formed of lower and / or upper disk, are arranged. Heat exchanger according to one of the preceding claims, characterized in that the housing ( 17 . 18 . 19 ) is formed at least in two parts and a housing shell ( 17a . 18a . 19a ) and a lid ( 17b . 18b . 19b ) having. Heat exchanger according to one of the preceding claims, characterized in that the inlet region ( 27 ) of the housing ( 21 ) an inlet nozzle ( 25 ), which in the housing shell ( 21a ) or is arranged in the lid. Heat exchanger according to one of the preceding claims, characterized in that the exit region ( 28 ) of the housing ( 21 ) an outlet nozzle ( 26 ), which in the housing shell ( 21a ) or is arranged in the lid. Heat exchanger according to one of the preceding claims, characterized in that the housing ( 21 ) Inlet and outlet nozzles ( 23 . 24 ) for the first fluid. Heat exchanger according to one of the preceding claims, characterized in that the inlet and outlet nozzles ( 23 . 24 . 30 . 31 ) for the first fluid in the lid ( 21b ) or in the housing shell are arranged. Heat exchanger according to one of the preceding claims, characterized in that the inlet and / or the outlet nozzle ( 25 . 26 ) Have longitudinal axes (A), which opposite the disc pairs ( 22 ) are inclined. Heat exchanger according to one of the preceding claims, characterized in that the heat exchanger has a bypass ( 56 . 57 . 58 . 59 ) having 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. 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. Heat exchanger according to one of the preceding claims, characterized that in the exit area for the second fluid is arranged a partition wall. Heat exchanger according to one of the preceding claims, characterized in that the heat exchanger contains at least one check valve, which is preferably integrated in the housing and in the outlet area ( 26 . 32 . 53 . 58 ) is located. Heat exchanger according to one of the preceding claims, characterized in that the bypass channel above ( 36 . 46 ) or below ( 34 . 42 ) of the pairs of discs ( 37 . 45 . 36 . 41 ) is arranged. 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 inserted into the housing. 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. 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 spaced. 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 passageway ( 5 ) Has projections, whereby preferably the flow channels ( 3 ) or the passageways ( 5 ) are substantially spaced from the bypass tube. 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 advantageous as a U-profile or half pipe. Heat exchanger according to one of the preceding claims, characterized in that the bypass channel ( 34 . 36 . 42 . 46 ) consists of two tube halves. 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. 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 integrable. Heat exchanger according to one of the preceding claims, characterized in that the inlet region has two separate inlet connection pieces ( 47 . 48 ) and a partition ( 49 ) having. Heat exchanger according to one of the preceding claims, characterized in that the pairs of discs a package ( 51 . 60 ), which can be flowed through in two bends by the second fluid. 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 exit chamber ( 53 ) and on the other hand the disk package ( 51 ) a deflection chamber ( 54 ) are arranged for the second fluid. Heat exchanger according to one of the preceding claims, characterized that the bypass in the case is integrated. Heat exchanger according to one of the preceding claims, characterized that the bypass is integrated in the lid. Heat exchanger according to one of the preceding claims, characterized that he has at least one flap. Heat exchanger according to one of the preceding claims, characterized that the flap is arranged in the entry area or in the exit area is. Heat exchanger according to one of the preceding claims, characterized that it has at least one bypass valve. Heat exchanger according to one of the preceding claims, characterized that the bypass valve into the housing is integrated. Heat exchanger according to one of the preceding claims, characterized that the bypass valve in the inlet area and / or in the exit area is arranged. Heat exchanger according to one of the preceding claims, characterized that the bypass valve is designed as a combination valve. Heat exchanger according to one of the preceding claims, characterized in that the integrated bypass a pivotable partition ( 59 ), by means of which the inlet nozzle ( 57 ) and the outlet nozzle ( 58 ) are short-circuited. Heat exchanger according to one of the preceding claims, characterized that the first fluid is a liquid Coolant, in particular the coolant from the cooling circuit an internal combustion engine of a motor vehicle and the second fluid recirculated exhaust gas the internal combustion engine is. Heat exchanger according to one of the preceding claims, characterized that the first fluid is air and the second fluid is recirculated exhaust gas of an internal combustion engine of a motor vehicle. Heat exchanger according to one of the preceding claims, characterized in that the heat exchanger is an oxidation catalyst ( 64 ) having. Heat exchanger according to one of the preceding claims, characterized in that the disk package ( 62 ) the oxidation catalyst ( 64 ) is connected upstream. Heat exchanger according to one of the preceding claims, characterized that the first fluid is a liquid Coolant, in particular the coolant the cooling circuit an internal combustion engine of a motor vehicle and the second fluid the internal combustion engine feedable Charge air is. Heat exchanger according to one of the preceding claims, characterized that the first fluid is air and the second fluid of an internal combustion engine a motor vehicle feedable Charge air is. Use of the heat exchanger according to one of the preceding claims as an exhaust gas cooler in an exhaust gas recirculation system an internal combustion engine of a motor vehicle or as a heater to Interior heating a motor vehicle. Use of the heat exchanger according to one of the claims previous claims as intercooler for direct or indirect cooling of Charge air for an internal combustion engine of a motor vehicle. Use of the heat exchanger according to one of the claims previous claims as an oil cooler to cooling of engine oil an internal combustion engine or transmission oil of a motor vehicle a liquid Coolant, preferably the coolant the cooling circuit the internal combustion engine. Use of the heat exchanger in particular according to one of the preceding claims as a refrigerant condenser in the refrigerant circuit an air conditioner for Motor vehicles. Use of the heat exchanger in particular according to one of the preceding claims as a refrigerant gas cooler in the Refrigerant circulation an air conditioner 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 an air conditioner for Motor vehicles.