JP2009501892A - Heat exchanger - Google Patents

Abstract

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

Description

  The present invention is a heat exchanger known from Japanese Patent Application Laid-Open No. H10-260260, and includes a flow passage capable of circulating a first fluid from a common first inlet to a common first outlet, and receiving these flow passages and The present invention relates to a heat exchanger including a housing capable of flowing a second fluid different from one fluid from a second inlet region to a second outlet region, and a flow passage having a flat cross section and a longitudinal side surface.

  The heat exchanger known from Patent Document 2 can be used as an exhaust cooler in an EGR system (exhaust gas recirculation system). Exhaust pipes are arranged in housings through which the liquid coolant of the internal combustion engine cooling circuit circulates, and these exhaust pipes are received at the ends in the pipe plates, which are themselves connected to the housing. Exhaust gas is supplied to the exhaust cooler via the diffuser, then flows through the exhaust pipe washed around by the coolant, and advances from the cooler via the exhaust fitting pipe. All parts of the exhaust cooler are brazed together. A disadvantage of this construction with a tube sheet that receives the tube end is that the tube is fixed in the tube sheet during the brazing process and cannot move relative to each other during brazing and melting of the wax layer, This has a disadvantageous effect on the brazing between the turbulent insert and the inner wall of the tube. This disadvantage is avoided by a tubeless system, as the following example shows.

  The heat exchanger known from US Pat. No. 6,057,097 can also be used as an exhaust cooler in an EGR system. The recirculated exhaust gas is cooled by a coolant taken from the cooling circuit of the automobile internal combustion engine. A known exhaust cooler has a substantially two-part housing, in which a cooling body made up of a large number of flat tube pieces capable of circulating coolant on the primary side is arranged. Circulate. The exhaust is guided in a relatively straight line, i.e. without any further turning. The coolant is supplied and discharged perpendicularly to the flat tube piece, and each 90 degrees of direction change occurs. In order to improve the heat transfer between the exhaust and the coolant, so-called turbulent plates are arranged between the flat tube pieces. The entire exhaust cooler consisting of the housing, the tube piece and the turbulent plate is produced by “integrated brazing”.

The object of application of patent document 1 starts from the prior art according to FIG. This prior art relates to an exhaust heat exchanger without a housing, in which a flat exhaust pipe is formed of a disk, and a folded edge portion of the disk is bent and has an edge plate standing on a longitudinal side surface, The plate is brazed with an adjacent border plate to form a housing wall. The disadvantage here is that there are a large number of brazing points, each brazing point leaking and therefore entailing the risk of exhaust leakage. The disadvantage of the patent application 1 is that the housing wall is directly subjected to an exhaust flow and is thus heated around the built-in exhaust cooler, for example to a temperature which is not favorable for the motor vehicle engine room.
German Patent Application No. 10060102 US Patent Application Publication No. 2003/0010479 German Patent Application No. 102004037391 German patent invention No. 19718064 German Patent Invention No. 19709601 German Patent Application No. 102005014295 German Patent Invention No. 10328746 German Patent Application No. 102005034136 German Patent Application Publication No. 1020050411149 German Patent Application No. 102005041150 German Patent Application Publication No. 102005034135 German patent invention No. 10321636 German Patent Invention No. 10321638 German Patent Application Publication No. 1020050411146

  The object of the present invention is to form a heat exchanger of the type pointed out at the beginning on the one hand in terms of joining technology, in particular by brazing, welding, bonding, etc., and on the other hand to lower its external temperature when using a high-temperature medium to be cooled. It is to suppress.

  This problem is solved by a heat exchanger characterized in that the longitudinal sides of the flow passages are joined to the housing in a material-joined manner, in particular by brazing, welding, bonding or the like.

BEST MODE FOR CARRYING OUT THE INVENTION

  According to the invention, the flow passages, which are mainly configured as disk pairs, are joined at their longitudinal sides to the housing wall in a material-joined manner, i. The disk pairs are stacked one above the other to form a bundle, and are connected to each other in terms of flow by lateral passages. A relatively high pressure loss occurs during the flow of these transverse passages, which on the one hand is due to a change of direction from the transverse passage to the passage surrounded by the disk pair, but in particular the transverse passage between the disk pair is generally By having sharp cutting edges, these cutting edges cause strong vortexing of the fluid and thus high pressure losses. Therefore, the disk pair distributes the first fluid, mainly liquid coolant, for which the pressure loss in the cooler is not so critical. The bundle of disk pairs is circulated with the second fluid, particularly the high-temperature medium to be cooled, flowing on the front side, and a relatively linear flow of the disk bundle, i.e., no significant change in direction, is achieved. Therefore, the pressure loss of the gaseous second fluid mainly decreases. A turbulent flow generation mechanism is provided between the disks in accordance with the heat transfer ratio. The heat exchanger according to the present invention is mainly brazed, welded, and bonded in one step. The parts to be brazed, welded or glued are arranged flexibly, i.e. moveable relative to one another, so that they can move relative to one another during the brazing process, in particular during melting of the wax layer, with minimal brazing A void and perfect brazing are achieved. Advantageously, the disk pairs can be pre-folded and / or pleated in the method steps preceding the joining process, in particular the brazing process, the welding process, the bonding process and the like. That is, a disk pair consisting of two disks, including a turbulent insert provided in some cases, is prepared in advance so that the disk pair is fixed by a side plate formed from one disk and surrounding the edge of the other disk. Both disc plates of a disc pair can no longer be misaligned with each other during the original brazing process and no longer move relative to each other or open mouth, thus ensuring a tight brazing of the disc pair Has been. For example, the pleated disc prevents the relative motion between the housing and the longitudinally abutting disc pair from different member heating and melting wax layers from causing inadequate brazing of the disc pair. be able to. As a result, tolerance adjustment between the longitudinal side surface of the disk pair and the housing is facilitated. This is because, during the brazing process, it is only necessary to ensure that the pleated disk pair still abuts the housing, and it is not necessary to take into account the possible mutual misalignment of both disks. It is. It is ensured that heat transfer between the first fluid, the cooling medium and the housing wall takes place due to the material-joint coupling of the flow passages or disk pairs. Due to the thermal coupling, the housing wall also contributes to the heat transfer, and the coupling of the disk pair significantly increases the heat transfer area for the second fluid depending on the geometry of the heat exchanger and the shape of the turbulence generator, If a turbulent plate is provided in the passage for the fluid, from about 2% to more than 10%, and a turbulence device (eg, a vortex body stamped into a disk) is utilized in the second fluid passage If done, it can be increased even to> 25%. An increase in heat exchanger performance is thus achieved and this increase can be substantial. Furthermore, the housing wall can be sufficiently cooled when a hot medium to be cooled is used, and can be kept at a relatively low temperature level. In many other heat exchanger applications, especially in the case of exhaust coolers, but also in the case of charge air coolers, sufficient cooling of the housing is often unavoidable. Otherwise, very high thermal stresses will occur at the joint between the housing and the disk pair, and these thermal stresses will be different and correspondingly different from the large temperature difference between the housing sending the exhaust and the cooled disk pair. This is due to thermal expansion. Another essential advantage of coupling the longitudinal sides of the disk pair to the housing is that the compressive strength of the heat exchanger is significantly increased with respect to the second fluid. This is because the disc means a tie rod that resists internal pressure between both housing sides. Thus, the heat exchanger concept is particularly suitable when the pressure loss requirements for the second fluid are very limited, the second fluid is very hot, or there is a high pressure of the second fluid, or This is for a medium in which a combination of requirements exists.

  In one configuration of the present invention, the flow passage is joined to the housing in a material joining manner over its entire length via a longitudinal side. The material joining type bonding is performed in particular by brazing, welding, adhesion or the like. Any other coupling scheme is basically possible, for example a mating coupling or a combination of material bonding and mating coupling.

  In one configuration of the invention, the flow passages are configured as disk pairs. The disk pair forms a second fluid flow-through passage. A coupling exists between the disk pair and the housing, and the second fluid has an inlet to the housing and the housing wall, thus cooling or heating the housing wall and the housing, for example.

  In one configuration of the invention, the flow passage and / or the flow-through passage are received by the housing substantially as a whole thereof, and the heat transfer between the first fluid and the second fluid is substantially completely covered by the lid. Occurs within the closable housing, as well as heat transfer between the second fluid and the housing and / or lid and between the first fluid and the housing and / or housing lid.

  In one configuration of the invention, at least one flow passage is formed between the lid and the adjacent disk, in particular the lower disk, for the fluid, in particular for the first fluid. Thus, the upper disk can be omitted and the lid is cooled together at the same time. Since the lid is connected to the housing by material joining such as brazing, welding, bonding, and / or by fitting such as molding, heat transfer from the lid to the housing and vice versa occurs and the housing is also cooled together Is done.

  In another configuration of the invention, at least one first fluid flow passage is formed between the bottom section of the housing or housing shell and the adjacent disk, in particular the top disk, between the bottom section of the housing shell. Thus, the disc, especially the lower disc, is omitted. In that case, the first fluid specifically cools the housing and the housing shell. However, it is also possible to couple the upper disk with the lower disk, in particular in a material-joint manner, so that the disk pair constituted thereby is via at least one disk, in particular via the lower disk adjacent to the bottom area, It is connected to the housing shell in the bottom region by a material joining type, particularly by brazing, welding, adhesion or the like.

  In one configuration of the present invention, the lower disk and the upper disk, each forming one disk pair, are connected to each other by a folding edge formed on the edge side, so that the disks are connected to each other in a fitting manner, in particular by bending. Has been. At least one disk, especially the lower disk, wraps another disk, especially the upper disk, so that the disk is locked in a nested manner, allowing simultaneous tolerance compensation in the stacking direction of the disk and disk pair, and material joining In the case of joining processes such as brazing, welding, gluing, etc., which create a formula bond, any opening or gap between the disks can be compensated, so that the joining process can be carried out successfully and reliably. A complete material joining is performed between the disks, in particular between the upper and lower disks, between adjacent pairs of disks and between the adjacent upper and lower disks.

  In one configuration of the invention, the inflow passage and / or at least one outflow passage extends across the disk pair, and the inflow passage and / or the outflow passage is zero with respect to the stacking direction of the disks and / or the longitudinal direction of the disks. It can extend into the disk pair at an angle of from ˜360 °, in particular from −50 ° to + 50 ° with respect to the stacking direction, with an angle of 0 ° with respect to the stacking direction being particularly advantageous. That is, the outflow passage and / or the inflow passage extend substantially parallel to the stacking direction. The angle of the outflow passage and the inflow passage relative to the stacking direction and / or the longitudinal direction can vary, and can be a value between 0 ° and 360 ° or −360 °.

  In one configuration of the invention, the disk pair has at least one bowl or at least one overhang. The pot body or the overhang portion is preferably provided on at least one disk of the disk pair, respectively, by a forming process such as bending and punching, or by primary forming or the like.

  In one configuration of the present invention, the projecting portion or the bowl of the disk pair reaches the adjacent disk pair, and the disk and the disk pair are in phase contact with each other, and are particularly connected to each other by brazing, welding, adhesion, etc. ing. Furthermore, a mating bond and / or a combination of a material bonded bond and a mating bond is possible as well as another bond.

  In one configuration of the present invention, the overhang portion or the bowl is provided on the upper disk by molding or primary processing, and the upper disk annular surface is the same, and this upper disk annular surface is connected to the lower disk of the adjacent disk pair. Contact with the lower disk annular surface provided by primary processing or molding process, and coupled with the lower disk annular surface, particularly by brazing, welding, bonding, etc., and / or mating joints such as locking, etc. Has been.

  In another configuration of the present invention, another overhang is provided on the lower disk, particularly by molding and / or primary processing, and the lower disk annular surface is the same, and the lower disk annular surface is the same as the adjacent disk pair. It is in contact with the upper disk annular surface of the upper disk and is connected to the upper disk annular surface, particularly by brazing, welding, bonding, etc. in a material joining manner and / or by a fitting joint such as locking.

  In one configuration of the invention, the flow passages are stacked. Similarly, the through-flow passages can be stacked. In one configuration, one disk is stacked on another adjacent disk, in particular the upper disk is mounted on the lower disk, the other lower disk is mounted on the upper disk, and the other upper disk is also mounted on the lower disk. Are stacked so that adjacent pairs of disks are stacked together. The disc stack or the stack of disc pairs is itself inserted into a housing shell which can be closed with a lid. The lid is placed on the housing, that is, the lid is placed on the housing in the stacking direction, especially by brazing, welding, bonding, etc. in the material joining type and / or by molding, locking, etc. in the mating joining type. Coupled with the housing, tolerance compensation can be performed in the stacking direction of the flow passages or flow-through passages during the joining process, in particular brazing, welding or bonding.

  In one configuration of the invention, the disks of the disk pair have a disk edge, the upper disk of the disk pair has an upper disk edge, the adjacent lower disk has a lower disk edge, and the upper disk edge. Corresponds to the lower disk edge surface and is connected to the material joining type by brazing, welding, adhesion or the like. The upper disk edge extends substantially parallel to the lower disk edge in the longitudinal direction of the disk, and similarly the upper disk edge extends in the direction of the disk width, which is substantially perpendicular to the disk longitudinal direction, and is particularly It is configured to be substantially perpendicular to the direction and substantially parallel to the lower disk edge. The joint of the lower disk edge surface and the upper disk edge surface is formed in the area where the longitudinal side surface of the disk transitions to the disk width in the stacking direction of the upper disk edge surface and the lower disk edge surface. It is configured as a substantially 1/4 cylinder in the longitudinal direction, and the 1/4 cylinder of the lower disk and the upper disk are contacted as two 1/4 cylinders that are substantially concentrically nested, especially in the material joining type They are connected by brazing, welding, bonding, etc.

  In one configuration of the invention, the longitudinal sides of the two disk pairs forming one flow passage at least partly wrap around the entire length of the disk, and the longitudinal sides contacting the housing are adjacent disks, in particular the other of each disk pair. Wrapping the long sides of the disc, thus both discs are pleated together.

  In one configuration of the invention, the wide sides of the two disk pairs forming one flow passage are at least partially wrapped around the full width of the disk. Both disks, in particular the upper and lower disks of the disk pair, are thus crimped together.

  In one configuration of the invention, the disk pair has a turbulent flow generating mechanism, particularly a turbulent insert or embossed structural element. The turbulent insert can be configured to be a braid comprising a plate with a punched portion and / or a wire. The contents of Patent Document 3, Patent Document 4 and Patent Document 5 are clearly disclosed.

  In one configuration of the present invention, the overhang portion is formed in a conical shape, and is implemented as a truncated cone generated from a disk mainly by a molding process such as punching or a primary process. The side of the frustum with the smaller diameter is configured as an annular surface, which contacts the adjacent disk, mainly the lower disk of the next pair of disks, in particular with the material joint. It is connected to the formula by brazing, welding, adhesion or the like.

  In one configuration of the invention, the overhang is streamlined, in particular with a longitudinal cross section or an elliptical cross section or a circular cross section.

  In one configuration of the present invention, a turbulent flow generation mechanism is inserted between the flow passages or in the flow-through passage. In this regard, the contents of Patent Document 3, Patent Document 4 and Patent Document 5 are still clearly disclosed.

  In one configuration of the invention, the folded edge connection is connected to the housing, particularly the inner surface of the housing, and this connection is made by brazing, welding, bonding, etc., particularly in a material joining manner.

  In one configuration of the invention, the inlet region of the housing is located upstream of the disk pair in the direction of flow of the second fluid.

  In one configuration of the present invention, the outflow region of the housing is disposed downstream of the disk pair in the flow direction of the second fluid.

  In one configuration of the invention, the disk pair is capable of flowing a second fluid around in parallel with its longitudinal side.

  In one configuration of the present invention, the long side-side folded edge is formed by bending the edges of the upper disk and the lower disk in the same direction. The longitudinal side-side folded edge portion further forms a housing contact surface.

  In one configuration of the present invention, the long side-side folded edge is formed by bending the edges of the upper disk and the lower disk in opposite directions. The longitudinal side-side folded edge portion further forms a housing contact surface.

  In one configuration of the invention, the disk pair has a first fluid side passage in the region of the housing wall on the long side.

  The side passage is configured as an extension of the flow cross section of the disk pair. The extension has a passage height that substantially matches the distance of the disk pair.

  In one configuration of the invention, the disk pair has a flow cross section with a passage width b, the housing wall has a distance w, b <w, and in particular between the flow cross section and the housing wall. And / or a material bridge formed of the upper disk is arranged.

  In one configuration of the present invention, the housing is composed of at least two parts and includes a housing shell and a lid.

  In one configuration of the invention, the inlet region of the housing has an inlet fitting tube disposed in the housing shell or lid. Furthermore, the outlet area of the housing has an outlet fitting tube that is arranged in the housing shell or in the lid.

  In one configuration of the present invention, the housing has a first fluid inlet fitting tube and an outlet fitting tube, the first fluid inlet fitting tube and the outlet fitting tube are arranged in the lid or in the housing shell, and are connected to the disk pair. And has a tilted longitudinal axis.

  In one configuration of the invention, the heat exchanger has a bypass. A second fluid bypass passage is disposed in the housing in parallel with the disk pair. For this purpose, the mass flow of the second fluid is divided into at least two partial mass flows, in particular by the separating wall, the at least one first partial mass flow of the second fluid flows in the through-flow passage and at least one first mass of the second fluid. A two-part mass flow flows through the bypass.

    In one configuration of the present invention, the disk pair forms a bundle capable of circulating the second fluid in two flow paths. Separation walls are arranged in the second fluid inlet region and / or in the second fluid outlet region. In particular, the separation wall is rotatably arranged so that the angle between the flow direction of the second fluid and the longitudinal side surface of the separation wall can be adjusted between 0 ° and 360 °.

  In one configuration of the invention, the heat exchanger includes at least one check valve, which is primarily integrated into the housing and in the outlet area.

  In one configuration of the invention, the bypass passage is located above or below the disk pair.

  In one configuration of the present invention, the bypass passage is configured as a bypass pipe that can be inserted into the housing. The bypass pipe is insulated from the flow passage (3) and / or the through-flow passage, in particular between the second partial mass flow flowing through the bypass passage and / or the bypass pipe and the first partial mass flow to be cooled in particular. The heat transfer is minimized as much as possible.

  In one configuration of the invention, the bypass pipe is substantially spaced from the flow passage and / or the flow-through passage. This separation is mainly effected by overhangs or punches inserted into the bypass pipe and / or the flow passage and / or the flow-through passage.

  In one configuration of the invention, the bypass tube consists of at least one partial element, which is configured mainly as an open cross-section, particularly preferably as a U-shaped cross-section or semi-tube.

  In one configuration of the present invention, the bypass pipe includes two pipe halves joined together by brazing, welding, bonding, etc., mainly in a material joining type.

  In one configuration of the invention, the bypass tube has at least one longitudinal separation wall.

  In one configuration of the invention, at least one bypass flap is integrated into the inlet or outlet region of the housing. The bypass flap is adjustable and can occupy an angle between 0 ° and 360 °, whereby the mass flow of the second fluid is divided into a first partial mass flow and a second partial mass flow. The first partial mass flow flows through the flow-through passage and is particularly cooled. The second partial mass flow flows through the bypass without being specifically cooled. The first partial mass flow of the second fluid in the through-flow passage is adjustable and / or controllable and / or adjustable by a bypass valve. The second partial mass flow of the second fluid in the bypass occurs depending on the regulated first partial mass flow and is therefore also controllable and / or adjustable.

  In one configuration of the heat exchanger, the inlet region has two separate inlet fitting tubes and one separating wall.

  In one configuration of the present invention, the disk pair forms a bundle capable of circulating the second fluid in two flow paths. An inlet chamber and an outlet chamber are arranged on one side of the disk bundle. A second fluid direction change chamber is disposed on the opposite side of the disk bundle.

  In one configuration of the invention, the bypass is integrated into the housing. In particular, the bypass is integrated with the housing.

  In one configuration of the invention, the bypass is integrated into the lid. In particular, the bypass is integrated with the lid.

  The heat exchanger according to any one of the preceding claims is characterized in that the flap is arranged in the inlet region or the outlet region.

  In one configuration of the invention, the heat exchanger has at least one bypass valve, which in particular controls and / or regulates the volumetric flow and / or mass flow of the second fluid in the bypass. The bypass valve is mainly integrated in the housing, in particular integrated with it. The bypass valve is arranged in the inlet region and / or the outlet region.

  In one configuration of the present invention, the bypass valve is implemented as a composite valve referred to below as a heat exchanger valve mechanism. In this heat exchanger valve mechanism, the valve disk rotates between a first opening position where the bypass outlet is closed and the heat exchanger outlet is opened, and a second opening position where the bypass outlet is opened and the heat exchanger outlet is closed. It is characterized by being possible. Even at high pressures, a sufficiently tight airtightness can be ensured by the rotatable valve disc.

  Another advantageous embodiment of the heat exchanger valve mechanism is that the pivotable valve disc has a fluid passage hole, which is at least partly in rotation with one of the other two fluid passage holes. The other two fluid passage holes are provided in the fixed valve disk relative to the valve housing. The three fluid passage holes are mainly configured identically to each other.

  Another preferred embodiment of the heat exchanger valve mechanism is characterized in that one of the fluid passage holes of the fixed valve disk communicates with the heat exchanger outlet and another fluid passage hole communicates with the bypass outlet. . Depending on the overlap of the fluid passage holes in the valve disc, more or less fluid will reach the bypass outlet or heat exchanger outlet, or not at all.

  Another preferred embodiment of the heat exchanger valve mechanism is characterized in that the fixed valve disc has a recess and a valve disc which can be rotated in this recess is guided. As an advantage derived from this, the valve disc guide of the valve housing can be omitted.

  Another preferred embodiment of the heat exchanger valve mechanism is characterized in that the fixed valve disk has a male thread and the fixed valve disk is screwed with this male thread into a complementary female thread of the valve housing. This facilitates the assembly of the fixed valve disk.

  Another preferred embodiment of the heat exchanger valve mechanism is characterized in that the actuator rod extends from a rotatable valve disk. This actuator rod, mainly drawn from the valve housing, facilitates the operation of the rotatable valve disk.

  Another preferred embodiment of the heat exchanger valve mechanism is characterized in that the valve disc is at least partly made of ceramic. Special steel can be used instead of ceramic.

  One preferred embodiment of the heat exchanger valve mechanism is a valve between a first extreme position where the bypass outlet is closed and the heat exchanger outlet is open and a second extreme position where the bypass outlet is open and the heat exchanger outlet is closed. It is characterized in that the slider can reciprocate. Even when the pressure is high, sufficient airtightness can be ensured by the valve slider.

  Another preferred embodiment of the heat exchanger valve mechanism is characterized in that the valve slider is partly made of ceramic. Special steel can be used instead of ceramic.

  Another preferred embodiment of the heat exchanger valve mechanism is characterized in that the valve housing is partly made of ceramic. The sliding surface for the valve slider is mainly made of ceramic.

  Another preferred embodiment of the heat exchanger valve mechanism is characterized in that the valve slider is equipped with an inlet sealing element. The inlet is mainly equipped with a sealing seat for the sealing element.

  Another preferred embodiment of the heat exchanger valve mechanism is characterized in that the sealing element has a sealing surface facing the inlet, the sealing surface having a spherical shape. The sliding of the valve slider is facilitated by using a sphere with a large diameter.

  In another preferred embodiment of the heat exchanger valve mechanism, the sealing element is guided reciprocally by a valve slider. This facilitates closing of the inlet with a sealing element, also called a closing element.

  Another preferred embodiment of the heat exchanger valve mechanism is characterized in that the sealing element is biased towards the inlet by a spring mechanism. This allows the inlet to be hermetically closed.

  Another preferred embodiment of the heat exchanger valve mechanism is characterized in that the valve slider has a pressure compensating passage. This facilitates sliding of the valve slider within the valve housing.

  In one configuration of the present invention, the integrated bypass has a swingable separation wall, and the inlet fitting tube and the outlet fitting tube can be short-circuited by this separation wall.

  In one configuration of the invention, the first fluid is a liquid coolant, in particular a coolant in a motor vehicle internal combustion engine cooling circuit, and the second fluid is a recirculation exhaust of the internal combustion engine.

  In one configuration of the present invention, the first fluid is air, and the second fluid is recirculation exhaust of an automobile internal combustion engine.

  In one configuration of the present invention, an oxidation catalyst as disclosed in Patent Document 6 is provided on the upstream side of the disk bundle. The entire contents of Patent Document 6 are clearly disclosed as such.

  In one configuration of the present invention, the first fluid is a liquid coolant, in particular, a coolant for an automobile internal combustion engine cooling circuit, and the second fluid is an air supply that can be supplied to the internal combustion engine.

  In one configuration of the present invention, the first fluid is air, and the second fluid is supply air that can be supplied to the automobile internal combustion engine.

  In one configuration of the invention, the heat exchanger is used as an exhaust cooler in an exhaust gas recirculation system of an automobile internal combustion engine or as an auxiliary heater for heating the interior of an automobile. At that time, heat transferred from the second fluid to the first fluid is used to heat the passenger compartment of the vehicle.

  In one configuration of the present invention, the heat exchanger is used as an oil cooler for cooling engine oil of an internal combustion engine or transmission oil of an automobile with a liquid coolant, mainly a coolant of an internal combustion engine cooling circuit.

  In one configuration of the invention, the heat exchanger is used as a refrigerant condenser in an automotive air conditioner refrigerant circuit.

  In one configuration of the invention, the heat exchanger is used as a refrigerant exhaust cooler in an automotive air conditioner refrigerant circuit.

  In one configuration of the invention, the heat exchanger is used as a refrigerant evaporator in an automotive air conditioner refrigerant circuit.

  Other advantageous configurations of the invention emerge from the dependent claims.

  One particularly advantageous configuration of the invention is the concept in which the edges of both disks of a disk pair are continuously configured in the circumferential direction and are in contact with each other in a plane (FIGS. 1, 2c, 3a, 3b, 3c). That means that both discs are shaped everywhere along their contact lines at the circumferential outer edge so that they have a mutual angle of 0 ° in a plane perpendicular to this contact line. Only can be described by being larger than 10 °. Both discs can abut each other in their contact line, for example in a plane, and both discs extend sufficiently parallel to each other over a certain section in a cross section perpendicular to the contact line. One disc or both discs can also be configured in a spherical shape in the area of the abutment line, for example, the contact between the straight line and the circular section in the cross section perpendicular to the contact line, or both are implemented in a spherical shape. In some cases, the point-like contact between two circular segments occurs only at one contact point, not at the contact line. Furthermore, both discs can be implemented, for example, such that their edges are formed concavely on one side and convexly on the other, so that there are two circular segments in a plane normal to the contact line, The two circular segments are either simply touching in a point or contact over a certain arc segment. All these embodiments accurately have a mutual angle of 0 ° in the circumferential contact line. Therefore, according to the present invention, the implementation of the disk pair can be formed very flexibly. This is because the second fluid flow passage is sealed everywhere on the longitudinal side by the housing, and therefore the outer edge of the disk pair does not require brazing with the adjacent disk edge. FIG. 2c shows the relationship between the process optimum disk pair configuration and the excellent thermal coupling of the housing to the first fluid passage that allows circumferential planar abutment between both disks at a small abutment angle. Show a good compromise.

  According to another advantageous configuration of the invention, the housing is composed of at least two parts, i.e. a housing shell which is, for example, a tank-like first housing part and a lid which is a lid-like second part. Yes. Both parts can be nested and can be easily joined together, in particular brazed, welded, glueed, etc. With such a housing concept, the housing parts are also nested or fitted in the stacking direction of the disk pairs, brazing, welding, gluing etc. during the joining process, especially brazing process, welding process, gluing process etc. When joined to the housing by means of an optimal joining process of stacked disk pairs, in particular a brazing process, a welding process, an adhesion process is also achieved. In a preferred implementation, the housing portion can then be brought as close to the disk pair as, for example, a melting wax layer does not cause gaps or brazing, welding and / or adhesion defects. Advantageously, the housing shell can also be manufactured as a molded part and / or primary part, for example a deep drawn part, like the lid, the housing shell forming a second fluid inlet and outlet region. You can also. Further, the inlet fitting tube and the outlet fitting tube can be formed as rim holes, for example, for the first fluid and the second fluid in the housing, whether the housing shell or the housing lid. The position and shape of the fitting tube can be arbitrarily selected according to the requirements for the heat exchanger. For the second fluid, the inlet fitting and the outlet fitting can be provided at the same cooler end or at opposite ends (see description below on this point), and inflow and outflow are in any arbitrary direction, for example cooling It can take place in the longitudinal direction of the vessel, here upwards from the lid, downwards from the housing or laterally from the housing.

  According to another advantageous configuration of the invention, a bypass passage can be arranged in the housing parallel to the disk bundle, the bypass being configured, for example, as a tube that is inserted into the housing and brazed to the rest of the parts. Can be kept. Such a bypass is particularly advantageous when using a heat exchanger as an exhaust cooler in an exhaust recirculation system. Such a bypass arrangement is known per se from the prior art, together with a corresponding bypass flap for controlling the exhaust flow in the heat exchanger or in the bypass. With the structure of the heat exchanger according to the invention, the bypass passage and the bypass flap can be integrated into the exhaust cooler by simple means. The fluid flow guided in the bypass must be guided separately from the fluid flow through the heat exchange passage also in the inlet region. For this reason, a separation plate or separation element, in the simplest implementation, a separation plate can be provided in the second fluid inlet region, the separation plate having two inlet regions, one for bypass fluid flow and the other for heat exchanger fluids. Separate for reuse. The separating element can for example be sandwiched, welded or brazed within the housing part or between the housing parts. The separated inlet regions can either have their own inlet holes in the housing or be supplied with fluid flow through a common inlet hole divided in two by the separating element. In the case of a common inlet hole, it is of course also necessary to separate both fluid streams at the second fluid supply, or the bypass flap can be placed directly in the inlet hole and closed directly at the separation element, from the bypass side. There must be no unacceptable leakage to the heat exchanger side and vice versa. This can be done, for example, by flanging a module consisting of a flap, a housing and an actuator. Further, the bypass flap can be integrated in the inlet region of the second fluid so that the gas flow can be directed directly into the bypass passage or heat exchange passage as required. In the case of such an integrated bypass flap, additional separation elements may still be required for sealing between the initial end of the bypass and the flap. All the above solutions can be provided with the same functionality, i.e. a separating element and a bypass flap in the arrangement and combination as well in the second fluid outlet region. In that case, what has been said about the need to separate the fluid flow in the supply applies equally to the discharge. All solutions are possible with compound valves instead of bypass flaps. That is, in addition to the induction of the fluid into the heat exchange passage or the bypass, the second fluid can be completely shut off. For example, the bypass flap or valve can be operated via an electric actuator or a U box (pressure operating element).

  The heat exchanger according to the invention allows a wide variety of implementations of the bypass passage. In one configuration of the invention, the bypass is inserted below the lowermost disk or above the uppermost disk in the stacking direction of the disk pair and is directly adjacent to the housing. In one configuration of the invention, the bypass is inserted into the housing from the other side of the stacked disk pair. In one configuration of the present invention, the bypass passage is integrally formed with the housing by embossing one or more longitudinal beads into the housing, the bypass passage formed thereby being confined on one side by the housing wall and opposite The side is limited by the first disk of the disk bundle. In one configuration of the present invention, a substantially U-shaped shell is mounted on the housing side and is joined to the housing, in particular, and brazed, welded, bonded, and the like to the bypass. The bypass is then confined between the mounted shell and the housing wall. Furthermore, the heat exchanger according to the invention can also be combined completely with an external bypass, ie a closed flow passage for the second fluid, which is connected to the heat exchanger, for example welded, waxed. It can be attached, or it can be fixed in a common holder with the heat exchanger. However, the external bypass can also be guided completely separate from the heat exchanger.

  In one configuration of the invention, any shape spacer such as corrugated or finned can be used between the disk stack and the housing wall. Furthermore, for example, a permeable structure such as a wire mesh or a porous material is conceivable. A shell that extends in the longitudinal direction, has a U-shaped cross section and opens towards the housing wall may be particularly advantageous. This shell supports the disk stack on the closed side.

  In one configuration of the invention, the structure forming the passage projects in the longitudinal direction into the inlet and / or outlet areas of the second fluid via the heat exchange passage formed by the stacked disks. Thus, a separation element between the bypass fluid stream and the heat exchanger fluid stream can be omitted. In one configuration of the present invention, the integrated bypass flap is configured such that no additional separation element is required for the bypass passage.

  The bypass passage must allow the passage of the second fluid on the side of the heat exchange passage without strong energy transfer from or to the first fluid and is therefore as well insulated as possible from the first fluid. Will have to. This insulation can be effected, for example, by supporting the bypass passage with a protrusion or bead against the housing wall and / or the disk stack. The protrusion or bead can be overhanged from a structure forming a bypass passage, such as a tube and / or a housing wall or a first disk adjacent to the disk stack. It is also possible to insert an additional insulator having a slight thermal conductivity (good insulating action) as an insulating element between the bypass passage and the adjacent structure. The insulating action is performed by an insulating material and / or by molding, in particular by a fin structure.

  In one configuration of the invention, the bypass passage is implemented with a double wall, specifically comprising a thick outer wall and a thin inner wall to carry. Both walls are formed such that the outer wall has a slight thermal stress than the inner wall.

  In another configuration of the invention, the heat exchanger can be circulated in two or multiple ways, i.e. the second fluid is divided into partial flows, each of which is parallel or directed within a part of the heat exchange passage. Be guided by the flow. In order to separate the partial streams, the same arrangement of separation plates and inlet / outlet holes as already described in the bypass pipe integration can be used.

  In one configuration of the present invention, the exhaust partial flow is guided by two flows from two cylinder banks. Thus, each pressure peak that occurs in the two streams can be used to increase exhaust recirculation rate and fuel efficiency when backflow to another stream is prevented. Therefore, backflow is blocked by check valves, which are integrated into the exhaust cooler, particularly in the outlet region of the second fluid, or in combination with a separator plate in the outlet region, in the outlet hole of the cooler housing. In particular, flanged.

  In one configuration of the present invention, the multi-path heat exchanger is configured to include a second fluid redirecting portion. The second fluid is not divided into partial flows, but is guided by one part of the fluid passage from the inlet end of the second fluid to another end, where it is redirected, in particular substantially 180 °, Returned again by another part. The turn can be done in several partial stages. However, it is also possible to provide a plurality of direction changing sections. When the number of direction changing sections is odd, the second fluid flows out at the inlet end of the heat exchanger. When the number of direction changing sections is even, the outflow flows through the heat exchanger. Done at the other end.

  In one configuration of the present invention, the direction change is performed as a U flow, and the inlet and outlet of the second fluid are narrowly arranged at one end of the cooler, so that the heat exchanger can be optimally integrated in the installation space. .

  In one configuration of the present invention, the heat exchanger is configured as a charge air intercooler between the compression stages of the turbo engine, and the direction change is performed by a housing connected to this end. No separation element or another turning element is configured.

  In one configuration of the present invention, no separate bypass pipe is required when configuring the U-flow. This is because the coupling between the inlet fitting and the outlet fitting in the combined inlet / outlet region of the cooler is shorted during bypass operation. In the case of the cooled exhaust gas recirculation, the path between the inlet fitting tube and the outlet fitting tube is blocked, and the second fluid, particularly the exhaust gas, is guided in the heat exchange passage.

  In one configuration of the invention, the heat exchanger with U-flow is implemented with an internal bypass flap and / or composite valve and / or an external bypass flap and / or composite valve. In an external bypass flap combined with a U-flow cooler, the separation of the inlet / outlet region can be provided by a separation element, in which case the bypass flap is particularly integrated into a module that can directly short the path in the exhaust cooler Has been.

  As already mentioned, the heat exchanger according to the invention can be used particularly advantageously as an exhaust cooler. In this case, cooling of the housing is particularly advantageous. This is because the coolant is partly in direct contact with the housing wall or indirectly connected to the housing wall via a material bridge. The cooling of the exhaust cooler can be effected by the coolant or air of the internal combustion engine cooling circuit, depending on its use in high pressure or low pressure exhaust recirculation (exhaust extraction upstream or downstream of the exhaust turbine) The adaptation of the heat transfer is for example done by a turbulent insert. When used as an exhaust cooler, it is advantageous to place an oxidation catalyst upstream of the disk pair in the exhaust flow direction, that is, at the inlet region of the exhaust cooler. The integration of the oxidation catalyst in the cooler outlet region upstream of the heat exchange tubes and possibly required bypass flaps is particularly significant in that case the flap / composite valve is protected from fouling.

  The heat exchanger according to the present invention can be advantageously used as a charge air cooler, whether it is direct cooling (air) or indirect cooling (liquid coolant). Furthermore, the heat exchanger according to the present invention can be advantageously used as a coolant-cooled oil cooler or as an air-cooled condenser of an automobile air conditioner. Only different media and heat transfer ratios need to be adapted for different uses.

  Furthermore, for the first medium, in addition to a simple connection scheme of both cocurrent flow between the first fluid and the second fluid or countercurrent flow between the first fluid and the second fluid (in which case U flow The cooler is a combination of both), and a plurality of circuits may be provided for the first fluid. For exhaust cooler applications, for example, it helps to prevent boiling efficiently, but the coolant flow can be guided parallel to the exhaust in the exhaust inlet region, and the coolant flow is Guided by exhaust and countercurrent, thus a particularly high rate of heat transfer is achieved in the rear part of the heat exchanger. Reference is made to U.S. Pat. Deriving the first fluid in the middle of the heat exchanger can be done through a common outlet for both circuits or through separate outlets. However, in order to improve heat transfer, for example, two circuits can be placed before and after the first medium, and both circuits can be circulated countercurrently to the second fluid. In that case, both circuits for the first medium have their own inlet and outlet.

  The concept with two circuits of the first fluid in countercurrent with the second fluid is particularly significant because the first medium and the second medium have similar heat capacities or the second medium is more than the first medium. This is when it has a high heat capacity, especially when both media are gases.

  Embodiments of the invention are shown in the drawings and are described in detail below.

  The heat exchanger 1 according to the present invention shown in FIG. 1 is configured as an exhaust cooler and can be used in an exhaust gas recirculation system (EGR system) of an automobile internal combustion engine. EGR systems are known from the prior art. Exhaust gas from the internal combustion engine is taken upstream or downstream (high pressure recirculation or low pressure recirculation) of the exhaust turbine, cooled in one or two stages, and supplied to the intake path of the internal combustion engine again. The amount of exhaust gas taken out is adjusted via an exhaust gas recirculation valve (EGR valve). The illustrated exhaust cooler 1 circulates exhaust gas and is cooled by a liquid coolant mainly taken out from the cooling circuit of the internal combustion engine. The exhaust cooler 1 has a two-part housing 2, which comprises a tank-like housing shell 2a and a lid 2b. Both parts are mainly constructed as thin plate parts and can be manufactured by deep drawing. A bundle of disk pairs 3 for circulating the coolant is disposed in the housing shell 2a. The disk pair 3 extends over the entire width of the housing shell 2a, which housing shell has two housing walls 2c, 2d which are shown perpendicular to the drawing and extend parallel to each other. The disk pair 3 has a longitudinal side 3a that abuts the housing walls 2c, 2d and forms a flow passage equipped with a turbulent insert 4 to enhance heat transfer. The disk pairs 3 are spaced apart from each other in parallel to form an exhaust through-passage 5. A turbulent insert 6 is arranged in the through-flow passage 5 to enhance heat transfer. All parts of the exhaust cooler 1 are joined together in a material-joint manner, i.e. by brazing. Brazing is mainly performed in a brazing furnace (not shown) in one step. Each disk pair has one upper disk 80b and one lower disk 80c.

  FIG. 2a shows another embodiment of the invention as part of an exhaust cooler. The same parts are denoted by the same reference numerals as in FIG. Two modified disk pairs 7 are arranged between both housing walls 2c, 2d, the disk pairs having their longitudinal sides 7a joined to the housing walls 2c, 2d by brazing. Each of the disk pairs 7 is composed of one upper disk 7b and one lower disk 7c, and both the disks are coupled to each other via a folding edge on the edge side. The flow cross section through which the coolant flows reaches the housing walls 2c, 2d, thus causing cooling of the housing wall heated by the exhaust flow.

  FIG. 2 b shows another embodiment of the present invention regarding the configuration of the disk pair 8. This disk pair is composed of upper disks 8a and 80b and lower disks 8b and 80c, and is closed by one folding edge 8c in the lateral direction. The flow cross section of the disk pair 8 is laterally expanded into side passages 8d and 8e, which side passages are generally at the height of the exhaust passage 5 or turbulent inserts 6 arranged in the exhaust passage 5. Have. At the same time, the side passages 8d and 8e for circulating the coolant extend from one disk pair 8 to the adjacent disk pair, and are in full contact with the housing walls 2c and 2d. This achieves a very good cooling of the housing walls 2c, 2d insulated from the exhaust flow. The same features are labeled with the same symbols as in the preceding figures.

  The other configuration of the disk pair 9 shown in FIG. 2c includes an upper disk 80b and a lower disk 80c between the housing walls 2c, 2d, and side passages 9a, 9b are formed by expansion of the flow cross section, however. The side passages do not have the entire height of the exhaust passage, but only a part, for example 50%. The remaining passage heights are bridged by the longitudinal folded edges 9c and 9d, respectively. Even in this implementation, the housing walls 2c, 2d are washed around by the coolant, so that a very good cooling of the housing walls can be obtained. The same features are labeled with the same symbols as in the preceding figures.

  FIGS. 3a, 3b, and 3c show another embodiment of the present invention relating to the configuration of the disk pairs 10, 11, and 12. Each disk pair is formed by one upper disk 80b and one lower disk 80c, and their flow. The width b of the passage is smaller than the inner width w of the housing. Disposed between the flow passages of the disk pairs 10, 11, 12 is a material bridge 10a, 10b, 11a, 11b, 12a, 12b, each extending in the longitudinal direction, each of which is a housing in various configurations. It abuts against the walls 2c and 2d and is brazed to them. As a result, a good cooling action, i.e. indirect cooling of the housing walls 2c, 2d, is achieved by heat transfer via the material bridges 10a, 10b, 11a, 11b, 12a, 12b. The same features are labeled with the same symbols as in the preceding figures.

  FIG. 4 is a three-dimensional view of the individual components of the exhaust cooler consistent with the embodiment of FIG. The same features are labeled with the same symbols as in the preceding figures. The housing shell 13 configured in a tank shape shown on the lower side of the drawing has an exhaust inlet hole 13a on the front side, that is, the short side surface thereof, and the exhaust gas (mostly hidden) on the short side surface on the opposite side. It has an exit hole 13b. Three disk pairs 14, one cover plate 15 and a housing lid 16 are shown above the housing shell 13. The disk pair 14 configured in a generally rectangular shape has edge pieces 14a bent at their longitudinal sides, and the edge pieces are formed as folded edges and can be brazed to the inner surface of the housing shell 13. The disk pair 14 circulates the coolant and thus has pot-shaped overhangs 14b, 14c. The overhanging portions each form one supply passage and one discharge passage for the disk pair when brazed, so that the passages can flow parallel to each other. A coolant connection (not shown here) is in the housing lid 16. It can also be seen from this figure that the individual parts of the exhaust cooler can be easily joined and prepared for the brazing process.

  Fig. 5a shows the disk pair 14 of Fig. 4 in a front view, i.e. another view as seen in the flow direction of the exhaust. The same reference numerals as in FIG. 4 are used. The disk pairs 14 are spaced apart in parallel and form a generally rectangular flow passage (through passage) 17 for exhaust. Here, the turbulent insert as shown in FIGS. 1 to 3 is omitted. Each disk pair 14 comprises two disks, namely an upper disk 14d and a lower disk 14e, both of which have their longitudinal sides joined together by a bent fold edge 14a. On the other hand, the front surface 14f forming the exhaust inflow ridge is connected to each other by a shallow folded edge. Thus, the disk pair 14 is sealed in the circumferential direction on the edge side. The pot-shaped overhanging portion 14b is formed from the upper disk 14d and abuts on the adjacent lower disk 14e. Thus, a coolant inflow passage or outflow passage is created that extends across the exhaust flow direction. The overhangs are streamlined to achieve a slight pressure drop on the exhaust side, for example—as apparent from FIG. 4—with an oval or elliptical cross section. Incidentally, depending on the application case, instead of the turbulent insert, a structural element in the form of a protruding piece or so-called winglet can also be formed on the disc.

  The unjoined disk pair 3, 14 shown in exploded view in FIG. 5b includes at least one upper disk 80b, at least one lower disk 80c and another lower disk 80c in the adjacent disk pair. The same features are labeled with the same symbols as in the preceding figures. Each of the upper disk 80b and the lower disk 80c has one disk hole 81 configured as a hole. The upper disk 80b includes at least one overhang 14b, in particular two overhangs 14b configured as a truncated cone in the stacking direction. The truncated cone includes upper disk annular surfaces 82 and 82c on the side of the smallest outer diameter, and the upper disk annular surface is parallel to the disk surfaces 92 of the upper disk 80b and the lower disk 80c and perpendicular to the stacking direction of the disk pairs 3 and 14. Is arranged. The lower disk annular surfaces 83 and 83c of the lower disk 80c are formed integrally with the disk surface 92, and are the same in the area of the disk hole. When joined, particularly brazed, welded, glued, etc., the upper disk annular surfaces 82, 82c of the disk pairs 3, 14 and the lower disk annular surfaces 83, 83c of the adjacent disk pairs 3, 14 are in contact with each other and are made of material. It is connected to the joint type. The upper disk 80b includes an upper disk edge surface 85 at the disk edge. The lower disk 80c includes a lower disk edge surface 86 at the disk edge. The upper disk edge surface 85 and the lower disk edge surface 86 coincide with each other, and are connected to each other by brazing, welding, adhesion, or the like in a material joining type. The upper disk edge surface 85 extends substantially parallel to the lower disk edge surface 86 in the longitudinal direction of the disk. Similarly, the upper disk edge surface 85 is particularly oriented substantially perpendicular to the longitudinal direction of the disk and substantially perpendicular to the disk stacking direction. It extends substantially parallel to the lower disk edge in the width direction. A joint 93 of the lower disk edge surface and the upper disk edge surface is formed in an area in which the disk long side surface of the upper disk edge surface and the lower disk edge surface transitions to the disk width in the stacking direction. The lower and upper disk quarter cylinders are substantially in contact as two nested concentric quarter cylinders, particularly brazed together in a material-joint manner, They are joined by welding, bonding, etc.

  FIG. 5c is an exploded view of an unjoined disk pair including at least one upper disk 80b and at least one lower disk 80c, a cross-sectional view taken along the line CC of FIG. 5b. The same features are labeled with the same symbols as in the preceding figures.

  FIG. 5d is a perspective view of the joined disk pair 3,14. The same features are labeled with the same symbols as in the preceding figures. When joined, particularly brazed, welded, glued, etc., the upper disk annular surfaces 82, 82c of the disk pairs 3, 14 and the lower disk annular surfaces 83, 83c of the adjacent disk pairs 3, 14 are in contact with each other and are made of material. It is connected to the joint type. The upper disk 80b includes an upper disk edge surface 85 at the disk edge. The lower disk 80c includes a lower disk edge surface 86 at the disk edge. The upper disk edge surface 85 and the lower disk edge surface 86 coincide with each other, and are joined to each other in a material joining type, particularly by brazing, welding, adhesion or the like. The upper disk edge 85 extends substantially parallel to the lower disk edge 86 in the longitudinal direction of the disk, and similarly the upper disk edge 85 is oriented substantially perpendicular to the longitudinal direction of the disk and substantially perpendicular to the disk stacking direction. It extends substantially parallel to the lower disk edge in the direction of the disk width. A joint 93 of the lower disk edge surface and the upper disk edge surface is formed in an area in which the disk long side surface of the upper disk edge surface and the lower disk edge surface transitions to the disk width in the stacking direction. The lower and upper disk quarter cylinders are substantially in contact as two nested concentric quarter cylinders, particularly brazed together in a material-joint manner, They are joined by welding, bonding, etc.

  FIG. 5e is a view of the joined disk pair as viewed in the flow direction of the second fluid. The same features are labeled with the same symbols as in the preceding figures.

  6a, 6b, 6c show various shapes for the construction of housings 17, 18, 19 having box-like or tub-like housing shells 17a, 18a, 19a, respectively. The same features are labeled with the same symbols as in the preceding figures. The lid shapes 17b, 18b, 19b are various. The circumferential protrusion (groove) 17c of the lid 17b can be placed on the upper circumferential edge of the housing shell 17a, and thus can be brazed. The lid 18b has a circumferential edge 18c standing up, which abuts against the inner wall of the housing shell 18a. Thus, the lid 18b can “sink” when brazed (when the wax layer of the disk bundle is melted). The lid 19b has a bent edge 19c, which wraps the upper ridge of the housing shell 19a from the outside, and thus can be brazed in the circumferential direction. All the parts shown can be manufactured as deep drawing parts at low cost.

  The exhaust cooler 20 shown in a longitudinal sectional view in FIG. 7 a includes a housing 21 including a housing shell 21 a, a lid 21 b, a first fluid inlet 90, and a first fluid outlet 91. A bundle 22 (shown by hatching) disposed in the housing 21 is formed of the disk pair (not shown), and the disk pair can circulate coolant. The same features are labeled with the same symbols as in the preceding figures. Corresponding coolant connecting portions are arranged as fitting tubes 23 and 24 on the lid 21 b of the housing 21. The exhaust gas indicated by the arrow A flows into the exhaust cooler 20 through the inlet fitting tube 25 and advances from the exhaust cooler via the outlet fitting tube 26. The inlet region 27 left on the upstream side of the disk bundle 22 in the exhaust flow direction functions as a diffuser, and the outlet region 28 left in the housing 21 on the downstream side of the disk bundle 22 is transferred to the outlet fitting tube 26. That is, the exhaust gas indicated by the arrow A flows in the exhaust cooler 20 or the disk bundle 22 in a substantially longitudinal direction (“axial direction”).

  Figure 7b shows a similar exhaust cooler 29, with the difference that the coolant connections 30, 31 are located on the bottom part of the cooler and the outlet side exhaust fitting 32 is located on the lid part of the housing, thereby As shown by arrow A, a 90 degree turn of the flowing exhaust can be achieved. The same features are labeled with the same symbols as in the preceding figures. Thus, such changes in exhaust and coolant supply or exhaust are possible by simple measures at the housing. 7a and 7b, the exhaust and coolant flows are shown as cocurrent. However, it is also possible to guide both media countercurrently to each other.

  8a and 8b show another embodiment of the present invention, in particular, an exhaust cooler 33 having a bypass passage 34 disposed below and an exhaust cooler 35 having a bypass passage 36 disposed above. Show. The same features are labeled with the same symbols as in the preceding figures. Both bypass passages 34, 36 can be configured as tubes and inserted into the housing and are parallel to the respective disk bundles 37a, 37b shown in hatching. The separation element or sealing element 38 that the exhaust cooler 33 according to FIG. 8a has in the exhaust inlet region serves to separate the exhaust stream into two partial streams, on the one hand for the disk bundle 37a and on the other hand for the bypass pipe 34. The exhaust cooler 35 according to FIG. 8b has an exhaust supply part with a 90 degree direction change part from the lid side. In response, a folded separation element 39 is arranged in the exhaust inlet region and seals the exhaust partial flows from one another. In both cases, a bypass valve (not shown) is arranged outside the exhaust cooler.

  FIG. 9 shows an exhaust cooler 40 according to another embodiment of the present invention. The exhaust cooler 40 includes a disk bundle 41 and a bypass passage 42 disposed below the disk bundle 41. As shown by an exhaust arrow A, the exhaust cooler 40 swings in the exhaust inlet region. A possible bypass flap 43 is arranged. The same features are labeled with the same symbols as in the preceding figures. Thus, the exhaust flow can be guided by either the disk bundle 41 or the bypass passage 42, and an intermediate position is also possible. The configuration of the bypass flap is also known by the prior art in terms of the exhaust branch.

  The exhaust cooler 44 shown in FIG. 10 as another embodiment of the present invention includes a disk bundle 45 (heat exchanging portion) and a bypass passage 46 disposed on the disk bundle 45, and is individually provided in the housing of the exhaust cooler 44. Exhaust inlets 47 and 48 are attached to the disk bundle and the bypass passage. The same features are labeled with the same symbols as in the preceding figures. A separation element or separation wall 49 arranged between both exhaust inlets 47, 48 can be brazed with the housing.

  11 shows another embodiment of the present invention, a two-way flow type exhaust cooler 50 includes a disk bundle 51 (heat exchange section), an exhaust inlet chamber 52, an exhaust outlet chamber 53 divided by a separation wall, and an exhaust flow direction change. The exhaust flow is indicated by a long solid U-shaped arrow A. The same features are labeled with the same symbols as in the preceding figures.

  FIG. 12 shows another embodiment of the present invention, that is, a two-way flow type exhaust cooler 55, which has an exhaust chamber 56 having an exhaust inlet fitting tube 57 and an exhaust outlet fitting tube 58. The same features are labeled with the same symbols as in the preceding figures. A swingable exhaust flap 59 (solid line) disposed in the exhaust chamber 56 can swing to a position 59 'indicated by a broken line. At the position 59, the inlet fitting tube 57 and the outlet fitting tube 58 are separated from each other. In other words, the exhaust flow flows through the heat exchanging portion 60 in accordance with the arrow A shown in the U shape and advances from the exhaust fitting tube 58. Thus, the entire exhaust stream is cooled. If exhaust cooling is not required, the exhaust flap 59 is moved to the position 59 ′ indicated by the broken line, and the exhaust gas flowing into the inlet fitting tube 57 is directly-short-circuited and directed to the outlet fitting tube 58 from the exhaust cooler 55. leak. In this way, the exhaust chamber 56 forms a bypass passage as shown by the broken arrow B. Thus, the disk bundle 60 can be bypassed by bypass. In other words, the exhaust cooler 55 has an integrated bypass with an integrated bypass flap.

  An exhaust cooler 61 shown in FIG. 13 as another embodiment of the present invention includes a heat exchanging portion 62 (disk bundle) capable of flowing exhaust through a single path (“axially”) in accordance with the exhaust arrow A. ing. The same features are labeled with the same symbols as in the preceding figures. The exhaust cooler 61 has an exhaust inlet region 63 configured as a diffuser, and an oxidation catalyst 64 arranged in this region serves for exhaust purification, as is known from the prior art. In this arrangement, in addition to the space-saving construction mode, it is possible to achieve exhaust flow rectification and thus improved addition of the disk bundle 62 provided downstream, by an exhaust passage (not shown) of the oxidation catalyst. it can.

  The exhaust cooler shown in FIG. 14 in longitudinal section is provided with two flows and one check valve for each flow in the outlet region of the second fluid. The same features are labeled with the same symbols as in the preceding figures. A second fluid first stream 87 and a second fluid second stream 88, which are configured in particular as a bypass, flow into a second fluid inlet region in the heat exchanger. The first stream 87 and the second stream 88 are separated and sealed from each other by a separating wall-like sealing element 89. The sealing element 89 is streamlined for the second fluid, and the flow flowing into the heat exchanger obliquely with respect to the longitudinal direction of the disk flows in the longitudinal direction of the disk until it reaches the inlet of the disk bundle by the rounded sealing element. Will be carried. The first check valve 94 for the first flow and the second check valve 95 for the second flow are integrated, particularly in the outlet region of the heat exchanger, and the first check valve 94 is first rotated adjacent to the bottom of the housing. The joint 98 is configured to be included. This rotary joint allows the first valve flap 96 to swing around a rotation axis arranged parallel to the disk width and perpendicular to the disk longitudinal direction. A second rotary joint 99 included in the second check valve 95 is disposed adjacent to the housing lid, and the second valve flap 97 swings around a rotation axis disposed parallel to the disk width and perpendicular to the disk longitudinal direction. Allow exercise. The second fluid is thus prevented from flowing back from the exit area back into the disk bundle.

  FIG. 15 is a DD longitudinal cross-sectional view of two pleated and bonded disk pairs. The same features are labeled with the same symbols as in the preceding figures. The upper disk 80b and the lower disk 80c are spaced substantially parallel to each other, and the distance between the upper disk 80b and the lower disk 80c of the disk pairs 3, 14 forms the height of the first fluid flow path, The distance between the lower disk 83 and the upper disk 82 of the adjacent disk pair forms the height of the second fluid flow passage. The lower disk 81c is configured with a hole 81, and a lower disk annular surface 83 is formed concentrically around the hole. The upper disk 81b also has a hole 81. In these hole regions, the conical overhanging portion 14b is formed in a conical shape perpendicular to the disk surface and from the upper disk in the stacked disk direction. The overhanging portion is bent in the area of the overhanging portion 14b having the smaller cone diameter of both cone diameters at both cone ends, and extends parallel to the disk surface. The upper disk annular surface 82 formed thereby contacts the lower disk annular surface 83 of the adjacent disk pair, and is connected to the material joint type by brazing, welding, adhesion or the like. The upper disk is bent in the direction of the housing bottom in the direction of the second fluid inlet region on the other side of the overhanging portion 14b. The height of the flow path is reduced, the upper disk 80b and the lower disk 80c of the disk pair are in contact with each other, extend in parallel with each other, and are joined to each other by brazing, welding, bonding, etc. The lower disk 80c extends in the longitudinal direction slightly beyond the length of the upper disk 80b, and the resulting end width region 101 of the lower disk 80c is at least partially around the upper disk 80b associated with the disk pair 3,14. It is folded over the entire width of the disc, thus wrapping the upper disc. This is called pleating. In addition, the pleating reduces flow loss when entering the disk pair as compared to when the second fluid enters the ridge. Similarly, on the exit side of the disk bundle, the lower disk is at least partially pleated with the upper disk over the entire disk width, but this is not illustrated in FIG. The pleating is also performed at least partly on both longitudinal sides of the disc, which is also not shown in FIG. In other embodiments, not shown, the upper disk may wrap around the lower disk.

  The exhaust cooler shown in FIG. 16 in a longitudinal sectional view has an exhaust flow direction change portion (two-way circulation), and one flow of fluid flows into the exhaust cooler and another flows out of the exhaust cooler. To do. The same features are labeled with the same symbols as in the preceding figures. The second fluid inlet and outlet are on the same side of the heat exchanger and are separated and sealed from each other by a sealing element 89 configured as a wall. The second fluid flows into the heat exchanger through the inlet / outlet region, and the direction change is performed as a U flow. The second fluid flows to the outlet region in the reverse flow direction and advances from the heat exchanger. The second fluid inlet and outlet are closely arranged at one end of the cooler, so that the heat exchanger can be optimally integrated in the structural space.

  In other implementations not shown, the turbulence generating element or turbulent insert is configured as a web fin.

Turbulent inserts with web fins have a relatively low tendency to collect deposits despite their basically small cross-sectional cross-section compared to other inserts. It had to be fundamentally concerned that turbulent inserts with web fins would strongly cause blockage of the individual flow-through passages due to the fine web fin structure. However, this is reasonable to an unexpectedly small extent, especially when the web of the web fin is relatively short. A possible explanation in this regard would be that particle deposition is reduced by exhaust turbulence that exists over most of the web fin insert. On the other hand, in the case of a vertically long monotonous passage, a stable flow is formed, which is near the wall, where the flow velocity is so low that it promotes particle deposition. The web fin web has a length that does not exceed about 10 mm, preferably does not exceed about 5 mm, and particularly preferably does not exceed about 3 mm. Depending on the given structural space and the internal combustion engine, there may be specific demands on the exhaust heat exchanger pressure drop. Depending on these requirements, one of the length ranges can be prioritized.

  Further, the density of web fins across the exhaust flow direction is between about 20 web fins / dm (decimeter) and about 50 web fins / dm, preferably between about 25 web fins / dm and 45 web fins / dm. . These web fin densities have been found to be particularly suitable in experiments. Web fins in particular are a particularly good compromise between the risk of blockage and the cooling capacity.

  As regards the height of the web fin, only a relatively small primary surface, i.e. a surface cooled by the coolant, is available for a large height, through which all heat is transferred to the coolant. Must be released. In that case, if the primary surface is relatively small, the risk of boiling increases in the case of a liquid coolant. In addition, the efficiency of the insert decreases with increasing web fin height. Therefore, the preferred height of the insert or web fin is about 3.5 mm to about 10 mm, particularly preferably about 4 mm to about 8 mm, particularly preferably about 4.5 mm to about 6 mm.

  In a preferred configuration of the apparatus according to the present invention, an oxidation catalyst can be arranged upstream of a number of flow passages. With such a catalyst, generally the particle size, particle density, and the proportion of hydrocarbons in the exhaust can be reduced by oxidation. Additionally or alternatively, the insert itself can be provided with a coating for catalytic oxidation of the exhaust. The web fin density that can be advantageously utilized across the exhaust flow direction, particularly in conjunction with the oxide catalyst means, can be greater than about 50 web ribs / dm, especially about 75 web ribs / dm. This will achieve a particularly large heat exchanger capacity in a given structural space without the long-term fear of blockage due to deposition.

  In a particularly preferred embodiment, the web fins are beveled. According to experimental results, the inclined fins are particularly suitable for ensuring a large long-term stability of the exhaust heat exchanger against deposition. In a preferred implementation, the angle between the web wall and the main direction of the web fin is between about 1 ° and about 45 °, and in a particularly preferred implementation this angle is between about 5 ° and about 25 ° This angle can also be between about 25 ° and about 45 °. The first indicated value range of 5 ° to 25 ° is particularly suitable for normal applications that are very sensitive to pressure loss. The second value range is suitable for achieving optimal power density, especially in applications that are less sensitive to pressure loss.

  When optimizing inserts with inclined web fins, it is generally possible to confirm the correlation between wall angle and web fin vertical pitch. A particularly optimal implementation can have a larger pitch I at small angles than an optimal implementation with a large angle. In particular, when the mounting angle is small, an implementation with a moderate pressure loss can occur. In particular, when the mounting angle is large, an implementation with an optimum power density can occur. In order to obtain optimum implementation, the vertical pitch can be increased, especially when the mounting angle is small, and the vertical pitch can be specially reduced when the mounting angle is large.

  In the preferred implementation, the apparatus is configured as a stacked disk heat exchanger. This embodiment deserves special consideration both with respect to the width of the flow passages of the heat exchanger housing with web fin inserts and with respect to cheap production and composites. However, alternatively, the device can also be configured as a tube bundle heat exchanger or as another heat exchanger embodiment known per se.

  In general, the insert is preferably made from stainless steel, in particular austenitic steel, to prevent corrosion due to corrosive exhaust.

  In another advantageous configuration, an aluminum material can be used, in which case it is particularly advantageous to provide suitable corrosion protection, in particular alloys and / or coatings.

  In one advantageous configuration, the insert is composed of aluminum. Aluminum inserts are extra lightweight. Particularly advantageously, the aluminum insert can be constituted by a corrosion-resistant alloy or coating.

  Depending on the flow parameters, in particular the Reynolds number, the length l / s of the flow path, in particular the inlet region of the tubes and / or stacked disc pairs, is approximately 2.5-5, and the length of the web fin is below this limit value. Must be selected. S is the average flow width between the two webs and is therefore b / 2-t, where t is the plate thickness. The required ratio is l / s <4, in particular l / s <2. If the risk of blockage is high due to dangerous exhaust composition, l / s <1.5, in particular l / s <1, can be selected.

  By slanting the web, on the twist side, higher flow velocities hit the walls and work against dredging. Another decisive advantage of the inclined web fin is that it requires a small density of web fins in the transverse direction of the flow to prevent occlusion, especially when the exhaust composition is inconvenient, despite the low fin surface area. Sufficient cooler capacity can be guaranteed.

  The stacked disk heat exchanger according to the present invention includes an outer housing with a lid, which is provided with an exhaust inlet and outlet and a liquid coolant inlet and outlet. A plurality of disk elements are provided inside the housing, and each disk element is composed of an upper half piece and a lower half piece. The disc elements are welded to each other and to the housing by means of the folded back, and the coolant flows from the inlet to the outlet, respectively, between the two halves of the disc pair. An insert (not shown) is disposed between the two disk elements with web fins, and the gaps between the two disk elements each form an exhaust flow passage. The insert is not shown for reasons of clarity. The insert is made of stainless steel. In order to improve the thermal contact between the insert and the disk element or housing, the insert can be welded or brazed planarly with the element.

  In another embodiment, the turbulent insert is made of a sheet material, and web fins parallel to the sheet material are provided by a molding procedure. Each web fin includes a series of webs arranged one after the other in the exhaust flow direction. Each of the two webs moving back and forth in the exhaust flow direction is arranged offset from each other by a half web width across the exhaust flow direction, and a cutting edge with subsequent webs follows each web. In this example, the walls are aligned parallel to the flow direction of the exhaust and form an angle of 0 ° with the axis B of the web fin or the main flow direction A of the exhaust. Such web fin inserts are referred to as straight tooth web fins.

  In the first embodiment, the length l of the web is about 4 mm. The width b of the individual web fins is defined as the width of the repeating unit of the periodic structure across the main flow direction of the exhaust. The web fin density 2 / b is about 40 web fins / dm in this example. Accordingly, the width b of one web fin is about 5 mm.

  The height h of the web fin corresponds to the distance between two adjacent disk elements of the heat exchanger, here about 5 mm.

  In that case, in other configurations of the web fin insert, the lateral walls of the individual webs are not aligned parallel to the main direction B of the web fins. Rather, each wall of the web forms an angle W of about 30 ° with the main direction B of the web fin. The other dimensions of the inclined web fin insert correspond to the dimensions of the straight web fin.

  Preferred implementations for producing a suitable longitudinal pitch l for the corresponding angle of the wall W are 10 <for a longitudinal pitch l <about 10 mm, l <about 6 mm for 20 °, l <about 4 mm for 30 °, 45 ° In this case, l <about 2 mm.

  The minimum vertical pitch I is about 1 mm at any angle. The permissible passage length l / s is generally within the same limits as the straight tooth web fin, where s represents the web distance across the main flow direction B. In general, it is difficult to manufacture a vertical pitch of l <1 mm for reasons of manufacturing technology.

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

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

  In the second embodiment, the charge air cooler and / or the exhaust cooler is an indirect charge air cooler and / or an indirect exhaust cooler. Indirect means that at least one medium to be cooled, such as exhaust and / or air supply, is cooled by a coolant such as a water-containing fluid and / or a liquid such as cooling water. This water-containing fluid and / or liquid such as cooling water is cooled by another cooling medium such as ambient air.

  In another embodiment, the at least one charge air cooler is directly cooled, the at least one exhaust air cooler is indirectly cooled, or vice versa, in another embodiment, the at least one charge air cooler is Indirectly cooled, the at least one exhaust cooler is directly cooled.

  In order to improve the heat transfer, in another embodiment at least two circuits, in particular 2, 3, 4 or more circuits for the first medium are put back and forth, ie in particular in the A direction and / or the disc. They are arranged in the stacking direction, and the stacking direction forms an angle of 0 ° to 90 ° with the A direction in particular. For example, the two, three, four or more circuits are circulated counter-current or co-current or at an angle of 0 ° to 90 ° with respect to the flow direction of the second fluid, in particular the second fluid.

  If the at least two circuits for the first medium, in particular two, three, four or more circuits, are arranged back and forth, i.e. in particular in the A direction, they are first arranged in the A direction flow. At least one high temperature circuit has a higher temperature than at least the second low temperature circuit. In particular, the temperature difference between the high-temperature circuit and the low-temperature circuit is 10K to 100K, in particular 30K to 80K, in particular 30K to 60K.

  The high temperature circuit has a temperature of 70 ° C. to 100 ° C., in particular 80 ° C. to 95 ° C., especially when in operation. The low-temperature circuit has a temperature of 10 ° C to 70 ° C, especially 20 ° C to 60 ° C, especially 30 ° C to 65 ° C, especially 40 ° C to 50 ° C, especially when in the operating state.

  Thus, the recirculated exhaust and / or charge or at least one cooled medium is cooled in two, three, four or more stages.

  Said at least two circuits for the first medium, in particular 2, 3, 4 or more circuits, are configured as at least one U-flow circuit and / or at least one I-flow circuit. For example, at least two I-flow circuits or at least two U-flow circuits are arranged in series, in particular before and after. In another example, at least one U-flow circuit follows at least one I-flow circuit, or vice versa. In particular, when at least two U-flow circuits are arranged, the coolant connection for the at least two circuits is in one example on one side of the cooler, for example up or down in the disk stacking direction, or 0 with respect to the stacking direction. It is arranged at an angle of from ° to 90 °.

  In another example, the forward flow is in the at least one hot circuit and the return flow is in the at least one cold circuit, or vice versa.

  In yet another embodiment, a compound valve comprises the at least one heat exchanger, such as an exhaust heat exchanger, and / or the at least one charge air cooler, and / or the at least one oil cooler, and / or Or the at least one coolant cooler and / or the at least one air conditioner refrigerant condenser, and / or the at least one air conditioner gas cooler, and / or the at least one air conditioner refrigerant evaporating. Integrated into and / or integrated with the at least one cooler for cooling the cooler and / or the electronic component, in particular the housing of the heat exchanger. The compound valve is a function of at least one exhaust recirculation valve for controlling and / or regulating the recirculated exhaust or exhaust-air mixture, and / or at least one bypass valve, in particular a bypass, for bypassing the recirculated exhaust. The functions of the flap and the at least one heat exchanger, in particular the exhaust heat exchanger and / or the further heat exchanger, are combined into one, the recirculation medium, in particular the exhaust and / or air, being the at least one heat. It is cooled in an exchanger, in particular an exhaust heat exchanger and / or one of said further heat exchangers. Such composite valves are disclosed in Patent Literature 8, Patent Literature 9, Patent Literature 10, Patent Literature 11, Patent Literature 12, Patent Literature 13, and Patent Literature 14, and the entire contents thereof are clearly disclosed. It is regarded as a thing.

  The features of the various embodiments can be arbitrarily combined with each other. The present invention can be used in fields other than the illustrated fields.

It is sectional drawing of the exhaust cooler based on this invention provided with the disk-shaped coolant channel | path. An embodiment relating to the configuration of the coolant passage for directly cooling the housing wall is shown. Fig. 5 shows another embodiment relating to the configuration of a coolant passage for directly cooling the housing wall. Fig. 5 shows another embodiment relating to the configuration of a coolant passage for directly cooling the housing wall. An embodiment relating to the configuration of the coolant passage for indirectly cooling the housing wall is shown. Fig. 5 shows another embodiment relating to the configuration of a coolant passage for indirectly cooling the housing wall. Fig. 5 shows another embodiment relating to the configuration of a coolant passage for indirectly cooling the housing wall. FIG. 3 is an exploded view of an exhaust cooler including a housing shell, a disk pair, and a lid. It is an exploded three-dimensional view of a disk pair and a lid. FIG. 3 is an exploded view of an unjoined disk pair including at least one upper disk, at least one lower disk, and another lower disk of an adjacent disk pair. FIG. 6C is a cross-sectional view of an exploded view of a pair of unjoined disks including at least one upper disk and at least one lower disk, taken along the line CC. It is a perspective view of the joined disk pair. It is the figure which looked at the disk pair joined in the flow direction of the 2nd fluid. Figure 2 shows an embodiment of a two-part housing of an exhaust cooler. Figure 2 shows an embodiment of a two-part housing of an exhaust cooler. Figure 2 shows an embodiment of a two-part housing of an exhaust cooler. It is a longitudinal cross-sectional view of the exhaust cooler provided with different exhaust and coolant guides. It is a longitudinal cross-sectional view of the exhaust cooler provided with different exhaust and coolant guides. It is a longitudinal cross-sectional view of the exhaust cooler provided with the bypass pipe and the separation wall integrated in the inlet region or the outlet region. It is a longitudinal cross-sectional view of the exhaust cooler provided with the bypass pipe and the separation wall integrated in the inlet region or the outlet region. It is a longitudinal cross-sectional view of the exhaust cooler provided with the bypass pipe and the integrated bypass flap. It is a longitudinal cross-sectional view of the exhaust cooler provided with the bypass pipe and two separate inlet fitting pipes. It is a longitudinal cross-sectional view of the exhaust air cooler provided with the direction change part (2 way distribution) of an exhaust flow. It is a longitudinal cross-sectional view of the exhaust cooler provided with the two-way distribution | circulation and the bypass integrated with the bypass flap. It is a longitudinal cross-sectional view of the exhaust cooler provided with the oxidation catalyst in the exhaust inlet region. FIG. 4 is a longitudinal sectional view of an exhaust cooler with two flows and one check valve for each flow in the outlet region of the second fluid. FIG. 4 is a DD longitudinal cross-sectional view of two pleated and bonded disk pairs. It is a longitudinal cross-sectional view of the exhaust cooler provided with the direction change part (2 way circulation) of an exhaust flow, The fluid in one flow flows in into an exhaust cooler, The fluid in another flow flows out from an exhaust cooler To do.

Claims (75)

  A flow passage capable of flowing the first fluid from the common first inlet to the common first outlet, and a second fluid that receives these flow passages and is different from the first fluid from the second inlet region to the second outlet. A heat exchanger having a flow passage having a flat cross section and a longitudinal side surface, wherein the longitudinal side surface (3a) of the flow passage (3) is a material joining type. A heat exchanger which is connected to the housing (2) by brazing, welding, adhesion or the like.   2. Heat exchange according to claim 1, characterized in that the flow passage (3) is joined to the housing material-joint over its entire length via a longitudinal side surface (3a), in particular by brazing, welding, bonding or the like. vessel.   The flow passages are configured as disk pairs (3, 7, 8, 9, 10, 11, 12, 14) and together with the housing (2) form a second fluid flow-through passage (5). The heat exchanger according to claim 1 or 2, characterized by the above.   A heat exchanger according to any one of the preceding claims, characterized in that the flow passage (3) and the flow-through passage (5) are received by the housing (2) substantially as a whole thereof.   At least one first fluid flow passage (3) is formed between the lid (2b, 16, 17b, 18b, 19b) and the lower disk (7c, 80c) adjacent to the lid. The heat exchanger according to any one of the preceding claims.   At least one first fluid flow passage (3) is formed between the upper disk (80b, 7b) adjacent to the bottom area of the housing shell (2a, 13) and the bottom area of the housing shell (2a, 13). A heat exchanger according to any one of the preceding claims, characterized in that   A lower disk (7c, 8b, 80c) in which a pair of disks (3, 7, 8, 9, 10, 11, 12, 14) are joined together on the edge side by folding edges (3a, 7a, 8c, 14a) and A heat exchanger according to any one of the preceding claims, characterized in that it has an upper disk (7b, 8a, 80b).   A heat exchanger according to any one of the preceding claims, characterized in that at least one inflow passage and / or at least one outflow passage extend across the disk pair (14).   Heat exchanger according to any one of the preceding claims, characterized in that the disk pair (14) has at least one bowl or at least one overhang (14b).   The overhanging portion (14b) of the disk pair (14) reaches the adjacent disk pair and is in contact with the adjacent disk pair, and is particularly connected to the adjacent disk pair by brazing, welding, adhesion, or the like. The heat exchanger according to any one of the preceding claims.   An overhang portion (14b) is provided on the upper disk (80b), and this overhang portion (14b) has an upper disk annular surface (82), and this upper disk annular surface is the lower disk (80c) of the adjacent disk pair. The lower disk annular surface (83) in contact with the lower disk annular surface (83) and connected to the lower disk annular surface by brazing, welding, bonding or the like, in particular, in a material joining manner. Heat exchanger.   The overhanging portion is provided on the lower disk (80c), and this overhanging portion has a lower disk annular surface (83c), and this lower disk annular surface is the upper disk annular surface ( Heat exchange according to any one of the preceding claims, characterized in that it is in contact with the upper disk annular surface (82c) in contact with 82c) and in particular in a material joining manner by brazing, welding, bonding etc. vessel.   A heat exchanger according to any one of the preceding claims, characterized in that the flow passages (3) are stacked.   The lid (2b, 16, 17b, 18b, 19b) is mounted on the housing (2) or the housing shell (2a, 13, 17a, 18a, 19a) in the stacking direction. The heat exchanger of any one of Claims.   The upper disk (80b) of the disk pair (14) has an upper disk edge surface (85), and the lower disk (80c) attached thereto has a lower disk edge surface (86), and this upper disk edge surface ( 85) A heat exchanger according to any one of the preceding claims, characterized in that 85) corresponds to the lower disk edge (86) and is joined in a material-joint manner, in particular by brazing, welding, bonding, etc. .   The longitudinal sides (3a) of the two disk pairs (14) forming one flow passage (3) at least partially wrap around the entire length of the disk, in particular the longitudinal side (3a) contacting the housing, in particular the adjacent disk, Heat exchanger according to any one of the preceding claims, characterized in that it wraps around the longitudinal side (3a) of the other disk of each disk pair.   Heat exchanger according to any one of the preceding claims, characterized in that the wide sides of the two disk pairs (14) forming one flow passage (3) at least partially wrap around the entire width of the disk .   Any of the preceding claims, characterized in that the disk pair (14) has a turbulence generating mechanism (4), in particular a turbulent insert or embossed structural element, arranged in the flow passage (3). The described heat exchanger.   A heat exchanger according to any one of the preceding claims, characterized in that the overhangs (14b, 84) are configured in a conical shape.   9. The overhang according to claim 1, wherein the overhangs (14b, 84) are streamlined in the direction of the longitudinal side surface (14a), in particular with a longitudinal or elliptical cross section. Heat exchanger.   Molded between turbulent flow generating mechanisms (6), in particular turbulent inserts, or disc pairs (3, 7, 8, 9, 10, 11, 12), between flow passages or in flow-through passages (5) A heat exchanger according to any one of the preceding claims, characterized in that a structural element is arranged.   The preceding claim, characterized in that the disk pair (3, 7, 14) is connected to the housing (2, 2c, 2d) via its longitudinal side-side folding connection (3a, 7a, 14a). The heat exchanger according to any one of the above.   The inlet region (27) of the housing (21) is arranged upstream of the disk pair (22) in the flow direction of the second fluid (A), according to any one of the preceding claims, Heat exchanger.   The outflow region (28) of the housing (21) is arranged downstream of the disk pair (22) in the flow direction of the second fluid (A), according to any one of the preceding claims. Heat exchanger.   Preceding, characterized in that the disk pair (3, 7, 8, 9, 10, 11, 12, 14) is capable of flowing a second fluid around parallel to its longitudinal side (3a, 7a, 14a) The heat exchanger according to claim 1.   Long side side folding edges (3a, 14a) are formed by bending the edges of the upper disk (14d) and the lower disk (14e) in the same direction, and form the contact surface for the housing (2, 2c, 2d) A heat exchanger according to any one of the preceding claims, characterized in that:   The long side surface side folding edge (7a) is formed by bending the edges of the upper disk (7b) and the lower disk (7c) in the opposite direction, and forms a contact surface for the housing (2c, 2d). The heat exchanger according to any one of the preceding claims.   The disk pair (8, 9) has a first fluid side passage (8d, 8e, 9a, 9b) in the region of the housing wall (2c, 2d) on the longitudinal side, according to the preceding claim The heat exchanger of any one of Claims.   29. A heat exchanger according to claim 28, characterized in that the side passages (8d, 8e, 9a, 9b) are configured as an extension of the flow cross section of the disk pair (8, 9).   30. A heat exchanger according to claim 29, characterized in that the extension (8d, 8e) has a passage height substantially corresponding to the distance of the disk pair (8).   The disk pair (10, 11, 12) has a flow cross section with a passage width b, the housing walls (2c, 2d) have a distance w, b <w, the flow cross section and the housing wall (2c, 2 d), a material bridge (10a, 10b), in particular formed of a lower disk and / or an upper disk, is arranged. Exchanger.   Any of the preceding claims, characterized in that the housing (17, 18, 19) comprises at least two parts and has a housing shell (17a, 18a, 19a) and a lid (17b, 18b, 19b) The heat exchanger according to claim 1.   Heat according to any one of the preceding claims, characterized in that the inlet region (27) of the housing (21) has an inlet fitting tube (25) arranged in the housing shell (21a) or in the lid. Exchanger.   Heat according to any one of the preceding claims, characterized in that the outlet region (28) of the housing (21) has an outlet fitting tube (26) arranged in the housing shell (21a) or in the lid. Exchanger.   A heat exchanger according to any one of the preceding claims, characterized in that the housing (21) has a first fluid inlet fitting tube (23) and an outlet fitting tube (24).   The first fluid inlet fitting tube (23, 30) and outlet fitting tube (24, 31) are arranged in the lid (21b) or in the housing shell, according to any one of the preceding claims. The described heat exchanger.   6. The inlet fitting tube (25) and / or the outlet fitting tube (26) according to any one of the preceding claims, characterized in that the longitudinal axis (A) is inclined with respect to the disk pair (22). Heat exchanger.   A heat exchanger according to any one of the preceding claims, characterized in that the heat exchanger has a bypass (56, 57, 58, 59).   A second fluid bypass passage (34, 36, 42, 46) is arranged inside the housing in parallel with the disk pair (36, 37, 41, 45). The heat exchanger of any one of Claims.   A heat exchanger according to any one of the preceding claims, characterized in that a separating wall (38, 39) is arranged in the inlet region for the second fluid.   The heat exchanger according to any one of the preceding claims, characterized in that a separation wall is arranged in the second fluid outlet region.   The heat exchanger comprises at least one check valve, the check valve being mainly integrated in the housing and in the outlet area (26, 32, 53, 58) The heat exchanger of any one of Claims.   A heat according to any one of the preceding claims, characterized in that the bypass passage is arranged above (36, 46) or below (34, 42) the disk pair (37, 45, 36, 41). Exchanger.   A heat exchanger according to any one of the preceding claims, characterized in that the bypass passage is configured as a bypass pipe (34, 36, 42, 46) insertable into the housing.   Heat exchanger according to any one of the preceding claims, characterized in that the bypass passage is insulated from the flow passage (3) and / or the through-flow passage.   Heat exchanger according to any one of the preceding claims, characterized in that the bypass passage is substantially spaced from the flow passage (3) and / or the through-flow passage.   The bypass passage and / or the flow passage (3) and / or the flow-through passage (5) adjacent to the bypass passage have protrusions, so that the flow passage (3) or the flow-through passage (5) mainly comes from the bypass pipe. A heat exchanger according to any one of the preceding claims, characterized in that it is spaced apart.   The bypass passage (34, 36, 42, 46) consists of at least one subelement, which subelement is mainly configured as an open cross section, particularly preferably as a U-shaped cross section or a semi-tube. The heat exchanger according to any one of the preceding claims.   A heat exchanger according to any one of the preceding claims, characterized in that the bypass passage (34, 36, 42, 46) consists of two pipe halves.   A heat exchanger according to any one of the preceding claims, characterized in that the bypass passage (34, 36, 42, 46) has at least one longitudinal separating wall.   A heat exchanger according to any one of the preceding claims, characterized in that a bypass flap (43) is integrated in the inlet or outlet region of the housing.   A heat exchanger according to any one of the preceding claims, characterized in that the inlet region has two separate inlet fitting tubes (47, 48) and one separating wall (49).   Heat exchanger according to any one of the preceding claims, characterized in that the disk pair forms a bundle (51, 60) through which the second fluid can flow in two flow paths.   The second fluid inlet chamber (52) and the outlet chamber (53) are arranged on one side of the disk bundle (51), and the direction changing chamber (54) is arranged on the opposite side of the disk bundle (51). The heat exchanger according to any one of the preceding claims.   A heat exchanger according to any one of the preceding claims, characterized in that the bypass is integrated in the housing.   A heat exchanger according to any one of the preceding claims, characterized in that the bypass is integrated in the lid.   A heat exchanger according to any one of the preceding claims, characterized in that the heat exchanger has at least one flap.   A heat exchanger according to any one of the preceding claims, characterized in that the flaps are arranged in the inlet region or in the outlet region.   A heat exchanger according to any one of the preceding claims, characterized in that the heat exchanger has at least one bypass valve.   A heat exchanger according to any one of the preceding claims, characterized in that the bypass valve is integrated in the housing.   A heat exchanger according to any one of the preceding claims, characterized in that a bypass valve is arranged in the inlet region and / or in the outlet region.   A heat exchanger according to any one of the preceding claims, characterized in that the bypass valve is implemented as a compound valve.   The preceding claim, characterized in that the integrated bypass has a swingable separating wall (59) by which the inlet fitting tube (57) and the outlet fitting tube (58) can be short-circuited. The heat exchanger according to any one of the above.   A heat exchanger according to any one of the preceding claims, characterized in that the first fluid is a liquid coolant, in particular a coolant for an automotive internal combustion engine cooling circuit, and the second fluid is a recirculation exhaust of the internal combustion engine.   The heat exchanger according to any one of the preceding claims, characterized in that the first fluid is air and the second fluid is recirculation exhaust of an automobile internal combustion engine.   A heat exchanger according to any one of the preceding claims, characterized in that the heat exchanger comprises an oxidation catalyst (64).   The heat exchanger according to any one of the preceding claims, characterized in that an oxidation catalyst (64) is provided upstream of the disk bundle (62).   Heat exchange according to any one of the preceding claims, characterized in that the first fluid is a liquid coolant, in particular a coolant of an automotive internal combustion engine cooling circuit, and the second fluid is an air supply that can be supplied to the internal combustion engine vessel.   The heat exchanger according to any one of the preceding claims, characterized in that the first fluid is air and the second fluid is an air supply capable of being supplied to an automobile internal combustion engine.   Use of a heat exchanger according to any one of the preceding claims as an exhaust cooler in an exhaust gas recirculation system of a motor vehicle internal combustion engine or as an auxiliary heater for heating the interior of a motor vehicle.   Use of a heat exchanger according to any one of the preceding claims as a charge air cooler for directly or indirectly cooling a charge air for a motor vehicle internal combustion engine.   Use of a heat exchanger according to any of the preceding claims as an oil cooler for cooling engine oil of an internal combustion engine or transmission oil of an automobile with a liquid coolant, mainly a coolant of an internal combustion engine cooling circuit .   Use of a heat exchanger according to any one of the preceding claims as a refrigerant condenser in a refrigerant circuit of an automobile air conditioner.   Use of a heat exchanger according to any one of the preceding claims as a refrigerant exhaust cooler in an automotive air conditioner refrigerant circuit.   Use of a heat exchanger according to any one of the preceding claims as a refrigerant evaporator in an automotive air conditioner refrigerant circuit.

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