Title of Invention	VALVE FOR REGULATING EXHAUST GAS FLOW OF AN INTERNAL COMBUSTION ENGINE AND A HEAT EXCHANGER
Abstract	"VALVE FOR REGULATING AN EXHAUST GAS FLOW OF AN INTERNAL COMBUSTION ENGINE, HEAT EXCHANGER FOR EXHAUST GAS COOLING, SYSTEM HAVING AT LEAST ONE VALVE AND HAVING AT LEAST ONE HEAT EXCHANGER" The invention relates to a valve (1, VT1) for regulating an exhaust gas flow of an exhaust gas flow of an internal combustion engine having at least one closure element, having at least one actuator for actuating the closure element, and having at least one heat transfer duct (30, 36) for valve cooling, which heat transfer duct can be traversed by at least one first medium (Ml).

Title of Invention

VALVE FOR REGULATING EXHAUST GAS FLOW OF AN INTERNAL COMBUSTION ENGINE AND A HEAT EXCHANGER

Abstract

"VALVE FOR REGULATING AN EXHAUST GAS FLOW OF AN INTERNAL COMBUSTION ENGINE, HEAT EXCHANGER FOR EXHAUST GAS COOLING, SYSTEM HAVING AT LEAST ONE VALVE AND HAVING AT LEAST ONE HEAT EXCHANGER" The invention relates to a valve (1, VT1) for regulating an exhaust gas flow of an exhaust gas flow of an internal combustion engine having at least one closure element, having at least one actuator for actuating the closure element, and having at least one heat transfer duct (30, 36) for valve cooling, which heat transfer duct can be traversed by at least one first medium (Ml).

Full Text	Valve for regulating an exhaust gas flow of an internal combustion engine, heat exchanger for exhaust gas cooling, system having at least one valve and having at least one heat exchanger The present invention relates to a valve for regulating an exhaust gas flow of an internal combustion engine according to' the preamble of claim 1 and to a heat exchanger for cooling exhaust gas having at least one valve, and a system having at least one valve and having at least one heat exchanger. In order to meet the current and future exhaust gas emission regulations, cooled exhaust gas recirculation is being used in diesel engines and/or spark ignition engines for passenger cars or for utility vehicles as a means of reducing the nitrogen oxide emissions (NOx) . Reliability problems of these systems are caused, for example, by failures or faults in a EGR valve which are due to the thermal loading by the hot exhaust gas stream or the formation of deposits from the exhaust gas stream. An EGR valve controls, in particular, the mass flow of recirculated exhaust gas which can flow through a heat exchanger, in particular an exhaust gas heat exchanger. The EGR valve can usually be actuated or activated electrically or pneumatically. The EGR valve can have various open-loop or closed-loop control positions. In a first position, the EGR valve prevents, for example, exhaust gas from flowing through the exhaust gas heat exchanger. In a second position, for example the entire mass flow of recirculated exhaust gas flows through the exhaust gas heat exchanger. In a third position of the EGR valve, a mass flow of recirculated gas flows through the exhaust gas heat exchanger, said mass flow being between zero mass flow of recirculated gas and the maximum mass flow of recirculated gas. The EGR valve can be arranged downstream or upstream of the heat exchanger, in particular of the exhaust gas cooler. In addition, the EGR valve can be arranged in, or adjacent to, the exhaust gas cooler. In a further embodiment, the EGR valve can be embodied in one piece with the heat exchanger, in particular the exhaust gas cooler. The EGR valve and the heat exchanger, in particular the exhaust gas cooler, can be arranged in a system having at least one internal combustion engine and at least one turbine, with which, in particular, a compressor for supercharging charge air or charge air and exhaust gas can be driven, on the outflow side of the turbine, i.e. on the low pressure side, or on the inflow side of the turbine, i.e. on the high pressure side. When the EGR valve is arranged on the inflow side of the heat exchanger, in particular of the exhaust gas cooler, the EGR valve is subjected to high temperature requirements owing to the hot exhaust gas. It is known in this context that the temperature requirement of the EGR valve can be reduced if the exhaust gas is not fed directly to the EGR valve from the exhaust section but instead the recirculated exhaust gas is not fed to the EGR valve and/or the exhaust gas heat exchanger until it has passed through the cylinder head of the engine. As a result of this routing of exhaust gas, heat is already extracted from the hot exhaust gas by the engine coolant before said hot exhaust gas is in contact with the EGR valve. Nevertheless, the EGR valve still experiences very high temperature loading. The arrangement of the EGR valve downstream of the exhaust gas cooler is usually selected in order to reduce the temperature loading of the EGR valve and of the corresponding actuator, in particular of the electrical or pneumatic actuator. However, it is disadvantageous here that the unburnt hydrocarbons (HC) which are contained in the exhaust gas form deposits on the EGR valve in conjunction with soot particles. As a result of the relatively low gas temperatures after the exhaust gas has flowed through the exhaust gas heat exchanger, the deposits which are formed in the EGR valve can be removed again only with difficulty since, for example, the deposits can only be burnt off with difficulty. The deposits cause the valve to become blocked due to sooting up or carbonizing and is therefore no longer functionally capable. On the other hand, arranging the EGR valve on the inflow side of the exhaust gas cooler makes it possible, owing to the high exhaust gas temperatures upstream of the exhaust gas heat exchanger, to burn off the deposits which are formed, for example in relatively high-load operating states of the internal combustion engine. However, the high temperature loading of the EGR valve also leads to heavy loading of the actuator. Even after the recirculated exhaust gas cools in the cylinder head, the actuator and EGR valve are still heavily loaded by the engine coolant. The applicant's unpublished document DE 102 005 029 322.0 discloses an EGR valve and an arrangement for recirculating and cooling exhaust gas of an internal combustion engine with an EGR valve. In one exemplary embodiment, the valve device is arranged here on the inflow side of a high temperature cooler, or in another exemplary embodiment the exhaust gas cooler is arranged on the outflow side. In addition, in the applicant's document DE 102 005 048 911.7, which is also still unpublished, an arrangement is disclosed for recirculating and cooling exhaust gas of an internal combustion engine in which an EGR valve is arranged on the outflow side of an exhaust gas cooler. In the applicant's document DE 102 005 049 309.2, which is also still unpublished. an EGR valve is disclosed, which has, in particular, an oxidation catalytic converter on the inflow side of an exhaust gas cooler. In the applicant's unpublished document DE 102 005 044 088.6, it is disclosed that an EGR valve is integrated into the inlet diffuser of a heat exchanger, in particular of an exhaust gas heat exchanger. The object of the present invention is to improve a valve of the type mentioned at the beginning. The object is achieved by means of the features of claim 1. Further advantageous refinements of the invention emerge from the subclaims and from the drawings. A valve is proposed for regulating an exhaust gas flow of an internal combustion engine which has at least one closure element and at least one actuator for activating the closure element, wherein the valve has at least one heat transfer duct for cooling the valve, through which heat transfer duct at least one first medium can flow. The at last one closure element can perform open-loop or closed-loop control on, in particular, a mass flow of a second medium such as, for example, exhaust gas. The closure element can be actuated by means of an actuator. The valve has at least one heat transfer duct for cooling the valve, through which heat transfer duct at least one medium, in particular coolant such as cooling fluid or air can flow or does flow. In one advantageous development, the heat transfer duct is embodied as an annular duct. The first medium, in particular cooling fluid or air, can particularly advantageously flow from an inlet opening to an outlet opening here. In addition it is possible to provide that the heat transfer duct has at least one wall pairing whose walls are embodied concentrically with respect to one another. In this way, the flow duct can particularly advantageously be formed in a plate by means of primary shaping fabrication methods such as, for example, injection molding, or by means of a material-removing fabrication method such as, for example, milling. In one advantageous development, the valve has at least a first opening for the inflow of the first medium and/or at least a second opening for the outflow of the first medium. In this way, the first medium can particularly advantageously flow through the heat transfer duct via the first opening, and the first medium can particularly advantageously flow out again from the second opening after it has flowed through the heat transfer duct. In addition it is possible to provide that the first medium is coolant, in particular a cooling fluid or air. In this way, the valve can be cooled particularly advantageously. Furthermore, it can particularly preferably be provided that the valve has at least one plate in which the heat transfer duct is arranged. In this way, the heat transfer duct can particularly advantageously be provided in the plate, for example by means of a primary shaping fabrication method such as injection molding, or by means of a material-removing fabrication method such as milling or drilling, and can particularly advantageously be connected to the valve. In a further advantageous embodiment, the plate has reinforcing devices and/or cavities in order to save weight. In this way, the plate can be made particularly lightweight. In addition it is possible to provide that the plate is connected to a valve housing in a materially joined and/or positively locking fashion. In this way, the plate can particularly advantageously be connected to the valve housing, for example by soldering, welding, bonding etc. and/or particularly advantageously connected in a positively locking fashion. In a further advantageous development, the plate is embodied in one piece with the valve housing. In this way, it is possible, in particularly advantageous way, to make savings in terms of assembly processes. In addition it is possible to provide that the plate has at least a first flange face for fastening purposes. It is particularly advantageously possible to fasten other components, for example an inlet diffuser and so on, to this flange face. A further advantageous refinement is characterized in that at least one aperture for preventing a flow around the heat transfer duct is arranged in the heat transfer duct. This can particularly advantageously prevent first medium, such as for example coolant or air, from flowing from the first opening, in particular the inlet opening, directly to the second opening, in particular to the outlet opening, and in the process not flowing through the heat transfer duct, as a result of which the valve element would not be correspondingly cooled. Furthermore, it can particularly preferably be provided that the valve has at least one sealing element, in particular a flat seal. This can particularly advantageously prevent media, such as for example the first medium, from escaping from the valve and/or other media entering the valve. According to the invention, a heat exchanger for cooling exhaust gas having at least one valve as claimed in one of claims 1 to 12 is also proposed. In one particularly preferred embodiment, the heat exchanger has a first flow duct through which the first medium and/or a second medium can flow. In this way, the first medium, which has in particular previously flowed through the valve, can particularly advantageously be made to flow through the heat exchanger, and/or a second medium can particularly advantageously be made to flow through the heat exchanger. Furthermore, it can particularly advantageously be provided that the heat exchanger has a second flow duct through which a third medium can flow. In this way, the third medium, such as for example exhaust gas, can particularly advantageously be made to flow through the heat exchanger, in particular, the exhaust gas heat exchanger. In addition, it is possible to provide that the second medium is a cooling fluid or air and/or the third medium is exhaust gas. In this way, the third medium, in particular exhaust gas, can be particularly advantageously cooled by the second medium, in particular the cooling fluid or the air. In one advantageous development, the heat exchanger has an inlet diffuser for the third medium. In this way, the third medium can in particular advantageously be made to flow through the heat exchanger via the inlet diffuser. In addition, it is possible to provide that the inlet diffuser has a second flange face which can be connected to the first flange face of the valve. In this way, the valve can particularly advantageously be connected to the heat exchanger. Furthermore, it can particularly preferably be provided that the sealing element for sealing the valve with respect to the inlet diffuser is arranged between the first flange face and the second flange face. In this way, the valve can particularly advantageously be sealed with respect to the inlet diffuser, and the inlet diffuser can particularly advantageously be sealed with respect to the sealing element. In a further advantageous refinement, the heat exchanger has at least one bypass valve to permit the third medium to bypass the heat exchanger. In this way, a third medium such as, for example, exhaust gas, can particularly advantageously not be directed through the heat exchanger, in particular the exhaust gas heat exchanger, but rather can be directed around it with the result that, particularly advantageously, it is possible to avoid cooling the exhaust gas. A further advantageous embodiment is characterized in that the at least one bypass valve can be activated by means of a second actuator. In this way, the bypass valve can particularly advantageously be activated by an electrical or pneumatic or hydraulic actuator. In addition it is possible to provide that the at least one bypass valve and/or the valve are arranged in, or adjacent to, the inlet diffuser. In this way, there can particularly advantageously be a saving in terms of installation space. According to the invention, in addition, a system having at least one valve as claimed in one of claims 1 to 12, and having at least one heat exchanger as claimed in one of claims 13 to 22, is proposed, which system has at least one internal combustion engine for ' ' a vehicle and at least a first turbine of an exhaust gas turbosupercharger, wherein the valve- is arranged on the inflow side of the heat exchanger and the heat exchanger is arranged on the high pressure side of the first turbine. In this way, the at least one heat exchanger, in particular the exhaust gas heat exchanger, and the valve can particularly advantageously be arranged on the high pressure side, with the result that the recirculation of exhaust gas can particularly advantageously take place on the high pressure side. According to the invention, in addition, a further system having at least one valve as claimed in one of claims 1 to 12 and having at least one heat exchanger as claimed in one of claims 13 to 22 is proposed, said valve having at least one internal combustion engine for a vehicle and at least a first turbine of an exhaust gas turbocharger, wherein the valve is arranged on the inflow side of the heat exchanger and the heat exchanger is arranged on the low pressure side of the first turbine. In this way, the at least one heat exchanger, in particular the exhaust gas heat exchanger, and the valve can particularly advantageously be arranged on the low pressure side of the turbine, with the result that the exhaust gas can particularly advantageously be cooled on the low pressure side. Furthermore, it can particularly preferably be provided that the system has at least a second heat exchanger for cooling charge air and/or the first turbine drives a compressor for supercharging charge air. In this way, the charge air in the second heat exchanger can particularly advantageously be cooled and/or the charge air can particularly advantageously be compressed by means of the compressor. In addition, it is possible to provide that the system has at least a second turbine which drives at least a second compressor for supercharging charge air. In this way, the charge air and/or the recirculated exhaust gas can particularly advantageously be supercharged or compressed in two stages. Further advantageous refinements of the invention emerge from the subclaims and from the drawings. The subject matters of the subclaims relate both to the valve according to the invention for controlling an exhaust gas flow of an internal combustion engine and to the heat exchanger according to the invention for cooling the exhaust gas having at least one valve, and to the system according to the invention having at least one valve and having at least one heat exchanger. Exemplary embodiments of the invention are illustrated in the drawings and will be explained in more detail below, whereby this is not intended to restrict the invention. In said drawings figure 1 is an isometric illustration of an exhaust gas heat exchanger with a coolable valve and a bypass valve, figure 2 is an isometric sectional illustration of a coolable plate of a valve, figure 3 is an isometric illustration of a coolable plate of a valve, figure 4 is an isometric illustration of a coolable plate of a valve having a sealing element, figure 5 is an isometric illustration of the bypass valve having an actuator, figure 6 is a sectionai liiustration A-A tnrougn tne bypass valve, figure 7 is a schematic illustration of a system having an exhaust gas heat exchanger and a coolable valve on the high pressure side with single-stage supercharging, figure 8 is a schematic illustration of a valve having an exhaust gas heat exchanger and a coolable valve on the high pressure side with two-stage supercharging, figure 9 is a schematic illustration of a system having an exhaust gas heat exchanger and a coolable valve on the low pressure side with single-stage supercharging, and figure 10 is a schematic illustration of a system having an exhaust gas heat exchanger and a coolable valve on the low pressure side with two-stage supercharging. The features of the various embodiments can be combined with one another as desired. The invention can also be used for fields other than those shown. Figure 1 is an isometric illustration of an exhaust gas heat exchanger 2 having a coolable valve 1 and a bypass valve 14. The valve 1 has at least one valve housing 7 and at least one plate 3, in particular cooling plate 3. The valve housing 7 has a valve housing flange 8, which is embodied essentially as a rectangular plate. In the illustrated exemplary embodiment, the corners of the plate are rounded, and in each case a valve housing flange bore 9 is provided adjacent to the corners (not denoted in more detail) of the valve housing flange 8. in the illustrated exemplary embodiment, four valve housing flange bores 9 are provided in the valve housing flange 8. In another exemplary embodiment, one to four or more than four valve housing flange bores 9 are provided in the valve housing flange. The valve housing flange bore can be embodied here as a cylindrical bore or a stepped bore or as a right-parallelepiped-shaped opening or as an oval or cylindrical bore or as a bore formed from a combination of the previously mentioned shapes. In another exemplary embodiment, the valve housing flange 8 is embodied as a round, in particular circular or oval plate, or for example as a star-shaped plate. The valve housing flange 8 can also be embodied as a plate which can be a combination of polygonal, square or rectangular and/or round or oval shapes. In the illustrated exemplary embodiment, the valve housing 7 is formed from the valve housing flange 8. The valve housing 7 is embodied essentially as a cylindrical section face from which a number of further cylindrical section faces and cylinders of different shapes and sizes are formed at different locations. In addition, a valve housing connecting flange 10 is formed from the valve housing 7. The valve housing connecting flange has a valve housing connecting flange opening 13. The valve housing connecting flange opening 13 is embodied essentially as a rectangular face with adjoining circular segments. In another exemplary embodiment, the valve housing connecting flange opening 13 can be embodied as a rectangular or square and/or circular or circular-segment-shaped and/or ellipsoidal opening. The valve housing connecting flange 10 has a frame (not denoted in more detail) , in which case, in the illustrated exemplary embodiment, the frame is a frame with circular segments or arc-shaped segments. In another exemplary embodiment, the frame (not denoted in more detail) can be rectangular or formed from rectangular elements and arcuate elements. In the illustrated exemplary embodiment, cylinder sections, which each have a valve housing connecting flange bore 12, are formed from the frame. For example, connecting elements, such as screws, can be plugged through the valve housing connecting flange bores 12. Other elements, for example an actuator or other valve elements, can be connected to the valve housing at the valve housing connecting flange 10 in a positively locking fashion, for example by screwing and/or in a materially joined fashion, for example by soldering, welding, bonding etc. In the illustrated exemplary embodiment, the valve housing connecting flange 10 has four valve housing connecting flange bores 12. In another exemplary embodiment, the valve housing connecting flange 10 has one to four or more than four valve housing connecting flange bores 12. Valve housing fastening eyelets 11 are formed from the valve housing 7. In the illustrated exemplary embodiment, three valve housing fastening eyelets 11 are formed from the valve housing 7. In another exemplary embodiment, one to three or more than three valve housing fastening eyelets can be formed from the valve housing 7. In the illustrated exemplary embodiment, the valve housing fastening eyelets 11 can be formed in one piece with the valve housing 7. Likewise, the valve housing connecting flange 10 and/or the valve housing flange 8 can be embodied in one piece with the valve housing 7 in the illustrated exemplary embodiment. In another exemplary embodiment, the valve housing flange 8 and/or the valve housing connecting flange 10 and/or the valve housing fastening eyelets 11 can be connected to the valve housing 7 in a materially joined fashion, for example by welding, soldering, bonding etc. In the illustrated exemplary embodiment, the valve housing and/or the valve housing flange 8 and/or the valve housing connecting flange 10 and/or the valve housing fastening eyelets 11 are manufactured by means of a primary shaping fabrication method such as, for example, injection molding. In another exemplary embodiment, the valve housing 7 and/or the valve housing flange 8 and/or the valve housing connecting flange 10 and/or the valve housing fastening eyelets 11 are formed by means of a material-removing fabrication method such as, for example, milling or turning or drilling. The valve housing 7 and/or the valve housing flange 8 and/or the valve housing connecting flange 10 and/or the valve housing fastening eyelets 11 can be formed from metal such as, for example, from steel, stainless steel or aluminum or from some other metal or from ceramic or from plastic or from a fiber composite material. The valve housing flange 8 is connected to the plate 3, in particular to the cooling plate 3 in a positively locking fashion, for example by screwing and/or in a materially joined fashion, for example by means of soldering, welding, bonding etc. The plate 3, in particular cooling plate 3, is arranged essentially parallel to the valve housing flange 8. In the illustrated exemplary embodiment, the plate 3 is embodied as a rectangular plate with rounded corners, in particular with four corners (not denoted in more detail). However, the plate 3 can also be embodied as a circular or cylindrical and/or oval element and/or from a combination of rectangular and cylindrical and/or oval or round elements. The inflow 4 is embodied as a cylindrical pipe in the illustrated exemplary embodiment. In another exemplary embodiment, the inflow 4 can be embodied as a pipe with a square or rectangular or polygonal cross section. In the illustrated exemplary embodiment, the inflow 4 is embodied in one piece with the plate 3. In another exemplary embodiment, the inflow 4 can be connected to the plate 3 in a materially joined fashion, for example by welding, soldering, bonding etc. and/or in a positively locking fashion. The outflow 5 is embodied essentially as a pipe. In the illustrated exemplary embodiment, the pipe has a circular cross section. In another exemplary embodiment, the pipe can have a rectangular or square or polygonal cross section or a cross section composed of rectangular and round and/or oval elements. In the illustrated exemplary embodiment, the outflow 5 is embodied in one piece with the plate 3. In another exemplary embodiment, the outflow 5 can be connected to the plate 3 in a materially joined fashion, for example by soldering, welding, bonding etc., and/or in a positively locking fashion. In the illustrated exemplary embodiment, the outflow 5 is connected to the cooling medium inlet 20 of the heat exchanger 2, in particular of the exhaust gas heat exchanger. In another exemplary embodiment, the outflow 5 is not connected to the heat exchanger 2, in particular to the exhaust gas heat exchanger. Therefore, on the one hand, the valve housing flange 8 of the valve housing 7 is arranged adjacent to the plate 3. On the other side lying opposite, an inlet diffuser 6 for the inflow of the third medium, in particular of the exhaust gas, into the heat exchanger 2, in particular into the exhaust gas heat exchanger, is arranged adjacent to the plate 3. The inlet diffuser is fluidically connected to a heat exchanger inlet diffuser flange 23. In the illustrated exemplary embodiment, the heat exchanger inlet diffuser flange 23 is embodied in one piece with the inlet diffuser 5. In another exemplary embodiment, the heat exchanger inlet diffuser flange 23 is connected to the inlet diffuser 6 in a materially joined fashion, for example by welding, soldering, bonding etc., and/or in a positively locking fashion. The heat exchanger inlet diffuser flange 23 is embodied in the illustrated exemplary embodiment as a parallelogram-shaped plate with an inlet opening (not illustrated). The corners of the parallelogram are essentially rounded. The inlet diffuser 6 is embodied in the illustrated exemplary embodiment from stainless steel or from some other steel. In another exemplary embodiment, the inlet diffuser 6 can be embodied from a metal with a low density, for example from aluminum or from ceramic or from an, in particular, heat-resistant plastic or from a fiber composite material. In the illustrated exemplary embodiment, the inlet diffuser 6 is embodied as a square with at least one cavity in the interior and with at least one opening (not illustrated) for the inflow of the third medium, in particular the exhaust gas. In another exemplary embodiment, the inlet diffuser is embodied, for example, as a pyramid, in particular as a four-sided or three-sided pyramid. In another further exemplary embodiment, the inlet diffuser 6 can be embodied as a cylinder with a circular or ellipsoidal cross-sectional area. In another exemplary embodiment, the inlet diffuser can be embodied from right-parallelepiped-shaped and/or cylinder-shaped elements and/or pyramid elements. The plate 3, in particular the cooling plate, is constructed from steel, in particular from stainless steel, in the illustrated exemplary embodiment. In another exemplary embodiment, the plate 3 can be constructed from ceramic or from a heat-resistant plastic or from a fiber composite material or from a metal with a low density such as, for example, from aluminum. The heat exchanger 2 is, in particular, an exhaust gas heat exchanger. In another exemplary embodiment, the heat exchanger 2 can be a coolant cooler and/or an oil cooler and/or a charge air cooler and/or a condenser for an air conditioning system and/or a gas cooler for an air conditioning system and/or a vaporizer for an air conditioning system. In the illustrated exemplary embodiment, the heat exchanger 2, in particular the exhaust gas heat exchanger, is constructed from metal, for example from a steel, in particular from stainless steel, and/or from a metal with a low density, for example from aluminum and/or from a plastic, in particular from a heat-resistant plastic, and/or from ceramic and/or from a fiber composite material. The heat exchanger 2, in particular the exhaust gas heat exchanger, has at least one heat exchanger housing 19. In the illustrated exemplary embodiment, the heat exchanger housing 19 is formed from a first right parallelepiped. The right parallelepiped has essentially a square cross-sectional area. On the two sides of the right parallelepiped which lie opposite one another, in each case a further right parallelepiped with a larger cross-sectional area than that of the first right parallelepiped which is located in the center between the two outer right parallelepipeds is formed from said right parallelepiped. The junction between the first right parallelepiped which is located in the center and the respectively adjoining outer right parallelepiped is embodied as a round junction. In another exemplary embodiment, this junction can also be constructed in a polygonal fashion such as for example as a shoulder. In the illustrated exemplary embodiment, the first right parallelepiped and the outwardly adjoining further right parallelepipeds are embodied in one piece. In another exemplary embodiment, the respectively outwardly adjoining right parallelepipeds can be connected in a positively locking and/or materially joined fashion, in particular by welding, soldering, bonding etc. In another exemplary embodiment, the heat exchanger housing 19 is composed as a cylinder or from a plurality of cylinder elements. In addition, in another embodiment the heat exchanger housing 19 can be embodied as a pyramid shape such as, for example, a three-sided or a four-sided or a multi-sided pyramid. In addition, in a further embodiment, the heat exchanger housing 19 can be constructed from conical segments or frustum-shaped segments. In a further embodiment, the heat exchanger housing 19 can be constructed from right-parallelepiped elements and/or pyramid elements and/or cylinder elements and/or conical elements or frustum elements. The heat exchanger 2, in particular the exhaust gas heat exchanger, has in its interior a number of pipes, in particular a number of flat pipes, through which the third medium, in particular the exhaust gas, flows and which are connected to an at least first base, in particular to two bases (not illustrated). The connection is positively locking, in particular by crimping or folding or chamfering and/or in a materially joined fashion, for example by welding, soldering, bonding etc. In the illustrated exemplary embodiment, the pipes (not illustrated), in particular flat pipes, are constructed from metal such as, for example, from steel, in particular from stainless steel, or from another material such as, for example, a metal with a low density such as aluminum, or from a fiber composite material or from a heat-resistant plastic. The flat pipes have a plurality of turbulence-generating elements such as, for example, winglets or other punched-out elements. These turbulence-generating elements may be produced, for example, in the flat pipes by means of a shaping fabrication method such as, for example, punching, stamping, pressing etc., or by a primary shaping fabrication method. In addition, turbulence inserts such as, for example, turbulence plates can also be provided in the flat tubes or between flat tubes. The tube plates (not denoted) are connected to the heat exchanger housing 19 by positive locking such as, for example, folding, beading, crimping etc. and/or in a materially joined fashion by, for example, welding, soldering, bonding etc. In another exemplary embodiment, the third medium, in particular the exhaust gas, flows between plates which can be stacked one on top of the other or are stacked one on top of the other. Between these plates it is possible to insert, for example, turbulence-generating elements such as turbulence plates which cause eddying of the flow and therefore lead to a better transfer of heat or a better transmission of heat. The plates can be connected to one another, for example, in a materially joined fashion by welding, soldering, bonding etc. and/or in a positively locking fashion by crimping or folding. At least one bypass valve 14 is arranged adjacent to the heat exchanger 2 and/or adjacent to the valve 1 and/or adjacent to the inlet diffuser 6. The bypass valve 14 has a valve element (not illustrated) which can be activated or is activated by means of a bypass valve actuator 15. The bypass valve element is adjusted between a plurality of positions or can assume a plurality of positions by means of a bypass valve lifting device 17 which can be activated or is activated by means of a bypass valve actuator 15. The bypass valve lifting device 17 has at least one bypass valve spring element 16. In the illustrated exemplary embodiment, the bypass valve spring element 16 is embodied as a helical spring. In another exemplary embodiment, the bypass valve spring element 16 can be embodied as a different spring element, for example as a leaf spring element etc. In the illustrated exemplary embodiment, the bypass valve 14 is integrated into the inlet diffuser 6 and/or into the heat exchanger 2, in particular into the exhaust gas heat exchanger. In another exemplary embodiment, the bypass valve 14 can be embodied as an independent add-on and is adjacent to the heat exchanger 2 and/or to the inlet diffuser 6 and/or can be connected to the heat exchanger 2, in particular to the exhaust gas heat exchanger and/or to the inlet diffuser 6 in a materially joined fashion, for example by welding, soldering, bonding etc. and/or in a positively locking fashion. In the illustrated exemplary embodiment, the heat exchanger 2, in particular the exhaust gas heat exchanger, has a coolant inlet 20 in one of the outer right parallelepipeds. Cooling medium, such as for example coolant, in particular aqueous coolant, or air, can flow into the heat exchanger 2 through this cooling medium inlet 20 and can flow through this heat exchanger 2, in particular the exhaust gas heat exchanger, and in the process cool the third medium, in particular the exhaust gas. The second medium, in particular the cooling medium, in particular the aqueous cooling medium or the air, flow around the flat pipes or the plates between which the third medium, in particular the exhaust gas, flows. The second medium, in particular the cooling medium flows in at least one flow duct (not illustrated) between the heat exchanger housing 19, in particular the heat exchanger housing wall, and the flat pipes or the plates. Turbulence-generating elements such as, for example, punched-out elements, knobs, winglets or turbulence plates, which are provided improve the transfer of heat in this context. The second medium, in particular the coolant. leaves the heat exchanger 2, in particular the exhaust gas heat exchanger, through an outlet opening (not illustrated) which is located on the underside of the heat exchanger housing 19, which underside cannot be seen in figure 1. In the illustrated exemplary embodiment, the cooling medium exits from the outer right parallelepiped which is located adjacent to the heat exchanger outlet diffuser 21. In another exemplary embodiment, the coolant inlet 20 is arranged on any desired side of the outer right parallelepiped or of the inner right parallelepiped. Likewise, in another exemplary embodiment, the first or second medium, in particular the cooling medium, flows out at any desired location on any desired side of one of the outer right parallelepipeds or at any desired location on any desired side of the inner right parallelepiped. In the illustrated exemplary embodiment, the outflow 5 of the first medium, in particular of the cooling medium, in particular of the aqueous cooling fluid or the air, is connected to the cooling medium inlet 20 of the heat exchanger 2, in particular of the exhaust gas heat exchanger. In another exemplary embodiment, the outflow 5 is not connected to the cooling medium inlet 20. In the illustrated exemplary embodiment, the third medium, the exhaust gas, which flows through the heat exchanger 2, is cooled by the first medium Ml, in particular the cooling medium, in particular the aqueous cooling fluid or air, and after the first medium Ml flows into the plate 3 via the inflow 4 it flows through the plate 3 and leaves the plate 3 via the outflow 5, flows through the pipe and the pipe bend into the cooling medium inlet 20 of the heat exchanger 2, in particular the exhaust gas heat exchanger, flows through it and in the process cools the third medium, in particular the exhaust gas, and leaves the heat exchanger 2, in particular the exhaust gas heat exchanger, again from the cooling medium outlet (not illustrated). The cooling medium 1 can subsequently be cooled, for example, by a coolant cooler and subsequently fed back again to the inflow 4 of the plate 3, in particular of the cooling plate 3. Figure 2 shows an isometric sectional illustration of a coolable plate 3 of a valve 1. Identical features are provided with the same reference symbols as in figure 1. In the illustrated exemplary embodiment, the plate 3, in particular the cooling plate, is embodied from a metal, for example stainless steel or from some other steel. In another exemplary embodiment, the plate 3 can be constructed from a metal with a low density such as, for example from aluminum or from a heat-resistant plastic or from ceramic or from a fiber composite material, The plate 3 is used to cool the valve 1 and/or a bypass plate (not illustrated) and its bypass plate actuator. Plate 3 has a plate outer wall 43 which is embodied, in particular, in a circumferential fashion. In the illustrated exemplary embodiment, the plate 3 is embodied as a pentagonal plate whose corners are rounded. In another exemplary embodiment, the plate 3 has sharp corners. In another exemplary embodiment, the plate 3 has a triangular, quadrilateral or polygonal shape. In another exemplary embodiment, the plate has a polygonal and/or round and/or oval cross-sectional area. The plate 3 can be manufactured by means of a primary shaping fabrication method such as, for example, injection molding, in particular metal injection molding, or by means of a material-removing fabrication method, in which case, in particular, cutouts and/or cavities and/or bores can be provided in the plate by means of a material-removing fabrication method such as, for example, drilling, milling, eroding etc. In the illustrated exemplary embodiment, the plate outer wall 43 is embodied essentially as a frame element. In this frame, the plate 3 has a wall pairing 31 which has at least a first plate wall 32 and a further second plate wall 33. The first plate wall 32 is embodied in the illustrated exemplary embodiment as a cylinder section which has a round cross-sectional area. The second plate wall 33 is also embodied in the illustrated exemplary embodiment as a cylinder section with a circular cross-sectional area. The first plate wall 32 has a larger cross-sectional diameter than the second plate wall 33. The annular duct 30 is formed between the first plate wall 32 and the second plate wall 33. The annular duct 30 is one possible embodiment of the heat transfer duct 36. In another exemplary embodiment, the heat transfer duct 36 can be embodied as a rectangular duct or as duct with a star shape or as a duct with a combination of arcuate and rectangular sections. The heat transfer duct 36 or the annular duct 30 is bounded in the plane of the first flange area 40 by the first heat transfer duct floor 45. The second plate wall 33 encloses a plate bore 44. The plate bore 44 is embodied in the illustrated exemplary embodiment as a through-bore. In another exemplary embodiment, the plate bore 44 can have a round and/or elliptical and/or rectangular and/or polygonal cross section. In the illustrated exemplary embodiment, the first plate wall 32 is embodied, at least in certain sections, in one piece with the plate outer wall 43. The rounded corners of the plate outer wall 43 have hollow-cylindrical formations which have fastening bores 42. The fastening bores 42 can contain, for example, threads. However, they can also be formed as bores without a thread. In the illustrated exemplary embodiment, the plate 3 has four of these formations with, in each case, one fastening bore 42. In another exemplary embodiment, the plate 3 can have one to four or more than four hollow-cylindrical formations, each with a fastening bore 42 or with more than one fastening bore 42. Reinforcing devices 37, which are embodied as reinforcement struts or reinforcing walls, extend from the plate outer wall 43 to the heat transfer duct 36 or to the annular duct 30. A plurality of these reinforcing devices 37 intersect here, extend at different angles with respect to one another and therefore reinforce the plate 3. The reinforcing devices 37 and/or the plate outer wall 43 enclose cavities 38 which have the purpose of reducing the weight of the plate 3. These cavities 38 can be provided in the plate 3 by primary shaping fabrication methods, with which the plate 3 is manufactured, or by a material-removing fabrication method such as eroding and/or drilling and/or milling. In the illustrated exemplary embodiment, the plate outer wall 4 3 and/or the reinforcing devices 37 and/or the first plate wall 32 and/or the second plate wall 33 and/or the aperture 41 and/or the inflow 4 and/or the outflow 5 can be embodied in one piece with the plate. In another exemplary embodiment, the elements which are mentioned in the previous sentence can, however, also be connected to the plate, for example by means of a materially joining method, such as for example soldering, welding, bonding etc. to the plate 3. The first medium Ml, in particular the cooling medium such as, for example, the aqueous coolant or air, passes into the plate 3 or into the heat transfer duct 36 or into the annular duct 30. In the illustrated exemplary embodiment, the aperture 41 is embodied as two projections, each projecting from the inner side of the first plate wall 32 in to the heat transfer duct 36 or into the annular duct 30, and the second projection is embodied such that it projects from the inner side of the duct in the second plate wall 33 into the heat transfer duct 36 or into the annular duct 30. The aperture 41 prevents the first medium from flowing directly from the' inflow and back into the outflow 5 again without predominantly flowing through the entirety of the heat transfer duct 36. In another exemplary embodiment, the aperture 41 can also be embodied as a continuous wall. The first medium Ml flows, after entering via the first plate opening 34 into the heat transfer duct 36 or the annular duct 30, through the heat transfer duct 36 or the annular duct and leaves it via a second plate opening 35 in order to flow out of the plate 3 again via the outflow 5. The plate 3 has a first flange face 40 on its underside. Opposite the first flange face 40 and essentially parallel thereto the plate 3 has a third flange face 39. The inflow 4 and/or the outflow 5 are embodied in the illustrated exemplary embodiment as a pipe with a round cross section. In another exemplary embodiment, the inflow 4 and/or the outflow 5 can be embodied as a pipe with an elliptical and/or rectangular and/or polygonal cross section. The inflow 4 and the outflow 5 have an angle a. The angle a can assume values between 1° and 180°, in particular between 10° and 150°, in particular between 20° and 120°, in particular between 30° and 100°, in particular between 35° and 90°, in particular between 40° and 70°. Figure 3 is an isometric illustration of a coolable plate 3 of a valve 1. Identical features have been provided with the same reference symbols as in the previous figures. In contrast to figure 2, figure 3 also has the second heat transfer duct floor 50. The heat transfer duct 36 or the annular duct 30 is surrounded at least in certain sections, by the first plate wall 32 (not illustrated), the second plate wall 33, the first heat transfer duct floor 45 (not illustrated) and the second heat transfer duct floor 50. Figure 4 is an isometric illustration of a coolable plate 3 of a valve 1 with a sealing element 60. Identical features have been provided with the same reference symbols as in the previous figures. In contrast to figure 3, figure 4 shows the plate 3, in particular the cooling plate, with a sealing element 60 which is arranged essentially parallel to and/or adjacent to the third flange face 39. The sealing element 60 is constructed from rubber or from some other plastic, in particular from an elastomer. The sealing element 60 is embodied as a flat seal in the illustrated exemplary embodiment. The sealing element 60 has first sealing bores 61 and second sealing bores 62. In the illustrated exemplary embodiment, the sealing element 60 has four second sealing bores 62 and two first sealing bores 61. In another exemplary embodiment (not illustrated) , the sealing element 60 may have one to four or more than four second sealing bores 62 and/or one to two or more than two first sealing bores 61. The first sealing bores 61 and the second sealing bores 62 are arranged essentially adjacent to the outer edge (not denoted) of the sealing element 60. In the illustrated exemplary embodiment, the sealing element 60 has an essentially rectangular face with rounded corners. In another exemplary embodiment, the sealing element 60 can have a round shape and/or a polygonal shape and/or an elliptical shape and/or a polygonal shape. In addition, the sealing element has a third sealing bore 63. The third sealing bore 63 has essentially the same diameter as the plate bore 44. The second sealing bore 62 has essentially the same diameter as the fastening bore 42. The diameter of the first sealing bore 61 is smaller than the diameter of the second sealing bore 62. In another exemplary embodiment, the first sealing bore 61 has a larger diameter than the second sealing bore 62. The third sealing bore 63 has a larger diameter than the first sealing bore 61 and/or the second sealing bore 62. In another exemplary embodiment, the third sealing bore can have a smaller diameter than the first sealing bore 61 and/or than the second sealing bore 62. Figure 5 is an isometric illustration of a bypass valve 14 with a bypass valve actuator 15. Identical features have been provided with the same reference symbols as in the previous figures. A heat exchanger housing section 70 of the heat exchanger 2, in particular of the exhaust gas heat exchanger, is embodied essentially as a right parallelepiped with rounded edges and an essentially square cross-sectional area. In another exemplary embodiment, the heat exchanger housing section 70 can have a rectangular and/or square and/or round and/or elliptical cross section. A tube plate 71, which is embodied essentially from stainless steel or from some other metal such as, in particular, aluminum, or from a heat-resistant plastic or from ceramic or from a fiber composite material, has a bypass opening 72 which is embodied essentially as an elongated hole. This bypass opening 72 is separated from a number of tube plate openings 73 by a bypass valve dividing wall 76. The tube plate openings 73 are embodied essentially as an elongated hole and have a smaller cross section than the bypass opening 72. A plurality of tube plate openings 73 are arranged in a grid shape in a plurality of rows and columns. Flat tubes (not shown) are plugged in through the tube plate openings 73 and are connected to the tube plate in a positively locking fashion by, for example, folding, beading, crimping etc. and/or in a materially joined fashion by welding, soldering, bonding etc. The third medium, in particular exhaust gas M3, in particular aqueous cooling fluid or air, flows to the bypass valve ■ element 75 in the direction of the arrow M3. The bypass valve element may assume various positions here. In a first position, the entire third medium M3 is fed through the tube plate opening 73, and the third medium M3 is not fed through the bypass opening 72. In a second position, third medium M3 is not fed through the tube plate openings 73 and the entirety of the third medium M3 is fed through the bypass opening 72. In a third position of the bypass valve element 75, third medium M3 is fed both through the tube plate openings 73 and through the bypass opening 72. In a fourth position of the bypass valve element 75, third medium M3 is neither fed through the bypass opening 72 nor through the tube plate openings 73. The bypass valve element 75 is actuated or activated essentially by the bypass valve actuator 15. The bypass valve actuator 15 has, in the illustrated exemplary embodiment, a housing (not denoted in more detail) which is composed of cylinder segments which are, in particular, arranged concentrically. The bypass valve actuator 15 activates a bypass valve lifting device 17 which activates the bypass valve element 75 via a bypass valve spring element 16. The bypass valve spring element 16 ensures that, after actuation via the bypass valve actuator 15, the bypass valve element 75 is moved back into a specific position. The heat exchanger housing section 70 has a coolant inlet 74 via which first medium, in particular coolant, such as, for example, aqueous cooling fluid or air or second medium, in particular aqueous cooling fluid or air, flow into the heat exchanger 2. In this context, reference is made to the still unpublished document DE 102 005 044 088.6 by the applicant in which a device for controlling an exhaust gas flow is disclosed. This is to be considered as constituting an express disclosure of the entire contents of the unpublished document DE 102 005 044 088.6 by the applicant. Figure 6 is a sectional illustration A-A through the bypass valve 14. Identical features have been provided with the same reference symbols as in the previous figures. The bypass valve 14 is arranged in a housing wall section 80. The housing wall section has a first stop 82 for the bypass valve element 81 and a second stop 83 for the bypass valve element 81. If the bypass valve element is located adjacent to the first stop 81 or if it is in contact, in particular, with the first stop 82, the third medium can flow into the bypass BP and not to the heat exchanger WT. If the bypass valve element 81 is arranged adjacent to the second stop 83, or the bypass valve element 81 is in contact with the second stop 83, at least in certain sections, the entirety of the third medium M3 flows to the heat exchanger, in particular the exhaust gas heat exchanger 2, and not to the bypass duct BP. If the bypass valve element 81 is in a position between the first stop 82 and the second stop 83, the third medium M3 flows both to the heat exchanger WT, in particular to the exhaust gas heat exchanger 2, and to the bypass duct BP. Figure 7 is a schematic illustration of a system with an exhaust gas heat exchanger AGK and a coolable valve VPl on the high pressure side with single-stage supercharging. Identical features have been provided with the same reference symbols as in the previous figures. The system illustrated in figure 7 shows an internal combustion engine M and a heat exchanger AGK, which corresponds to the heat exchanger 2, in particular the exhaust ga=; heat exchanaer. In addition, the system has a valve VTl, which corresponds to the valve 1. Air which is sucked in from the outside, which is at the pressure NDl, the low pressure, is compressed, by means of a first compressor VI which is driven by means of a first turbine, to the relatively high pressure HD, the high pressure. The turbine Tl and the compressor VI are embodied as a turbocharger. The air which is compressed to the high pressure HD warms up and is cooled in the charge air cooler LLKl. The cooled charge air has recirculated and cooled exhaust gas fed to it and the mixture of charge air and exhaust gas is fed into the combustion engine M. Exhaust gas leaves the combustion engine M and some of the exhaust gas is fed to the first valve VTl, the valve 1, in particular the EGR valve, and subsequently cooled in the heat exchanger AGK, in particular the heat exchanger 2, in particular the exhaust gas heat exchanger, and added again to the compressed and cooled charge air. In figure 7, the supercharging of the charge air takes place in a single stage by means of the compressor VI and/or by means of the turbocharger. Figure 8 is a schematic illustration of a system with an exhaust gas heat exchanger AGK and a coolable valve VTl on the high pressure side with two-stage supersupercharging. Identical features have been provided with the same reference symbols as in the previous figures. In contrast to figure 8, the at the pressure level ND2 is compressed from the low pressure level to the low pressure level NDl by the compressor V2. The compressed air heats up during this and is cooled in the charge air cooler LLK2 and compressed by the compressor VI to the high pressure level HD. The compressor VI is driven by the first turbine Tl, which relaxes part of the exhaust gas from the high pressure level HD to the low pressure level NDl. In addition, the compressor V2 is driven by the second turbine T2, which relaxes part of the exhaust gas from the low pressure level NDl to the low pressure level ND2. Both in figure 7 and in figure 8, the valve VTl, in particular valve 1, is arranged on the inflow side of the heat exchanger AGK, in particular of the exhaust gas heat exchanger 2. Both in figure 1 and in figure 8, the valve VTl is embodied as a separate structural unit upstream of the exhaust gas heat exchanger AGK, in particular the heat exchanger 2. In another exemplary embodiment, the valve VTl can be embodied in one piece with the exhaust gas heat exchanger AGK, or integrated into it. In another exemplary embodiment, the valve 1, VTl, can also be arranged on the outflow side of the heat exchanger AGK, 2. Figure 9 is a schematic illustration of a system with a heat exchanger AGK and a coolable valve VTl on the low pressure side with single-stage supersupercharging. Identical features have been provided with the same reference symbol as in the previous figures. In contrast to figure 7, the coolable valve VTl, in particular the valve 1 and/or the heat exchanger AGK, in particular the exhaust gas heat exchanger 2, are arranged on the low pressure side, i.e. the outflow side of the first turbine Tl. In the illustrated exemplary embodiment, the valve VTl, in particular the valve 1, is arranged as a separate structural unit on the inflow side of the heat exchanger AGK, in particular of the exhaust gas heat exchanger 2. In another exemplary embodiment, the valve VTl is embodied in one piece with the heat exchanger AGK, in particular the exhaust gas heat exchanger 2, and/or integrated into it. Figure 10 is a schematic illustration of a system with a heat exchanger AGK and a coolable valve VTl on the low pressure side with two-stage supersupercharging. Identical features have been provided with the same reference symbols as in the previous figures. In contrast to figure 9, the valve VTl and/or the heat exchanger AGK, in particular the exhaust gas heat exchanger 2, are arranged in the low pressure region ND2. The valve VTl, in particular the valve 1, is arranged on the outflow side of the second turbine T2, as is the exhaust gas heat exchanger AGK, in particular the exhaust gas heat exchanger 2, with the valve VTl being arranged as a separate structural unit on the inflow side of the heat exchanger AGK. In another exemplary embodiment, the valve VTl, in particular the valve 1, can be embodied in one piece with the heat exchanger AGK, in particular the exhaust gas heat exchanger 2, and/or integrated into it. Sucked-in air is mixed with the cooled, recirculated exhaust gas and compressed in the second compressor V2 to the low pressure level NDl and subsequently cooled in a second charge air cooler LLK2 and compressed in a first compressor VI to the high pressure level HD. The valve 1, VTl, can be embodied as a slide valve, for example as in the unpublished document DE 102 005 041 149.5, the entire content of which is to be considered as having been disclosed herewith. In addition the valve 1, VTl, can be embodied as a valve, as is disclosed in the unpublished document DE 102 005 041 150.9 by the applicant, the entire content of which is to be considered as being expressly disclosed herewith. The valve 1, VTl can also be embodied as a valve as is disclosed in the unpublished document DE 102 005 044 089.4 by the applicant, the entire content of which is to be considered as expressly disclosed herewith. In addition, the valve 1, VTl, can also be embodied as a valve such as is disclosed in the unpublished document DE 102 005 058 494.2 by the applicant, the entire content of which is to be considered as expressly disclosed herewith. The features of the various exemplary embodiments can be combined with one another as desired. The invention can also be used for fields other than those indicated. WE CLAIM 1. A valve for regulating an exhaust gas flow of an internal combustion engine, having at least one closure element and at least one actuator for activating the closure element, characterized in that the valve (1, VTl) has at least one heat transfer duct (30, 36) for cooling the valve, through which heat transfer duct (30, 36) at least one medium (Ml) can flow. 2. The valve as claimed in claim 1, characterized in that the heat transfer duct (36) is embodied as an annular duct (30). 3. The valve as claimed in one of the preceding claims, characterized in that the heat transfer duct (30, 36) has at least one wall pairing (31) whose walls (32, 33) are embodied concentrically with respect to one another. 4. The valve as claimed in one of the preceding claims, characterized in that the valve (1, VTl) has at least a first opening (34) for the inflow (4) of the first medium (Ml) and/or at least a second opening (35) for the outflow (5) of the first medium (Ml). 5. The valve as claimed in one of the preceding claims, characterized in that the first medium (Ml) is coolant, in particular a cooling fluid or air. 6. The valve as claimed in one of the preceding claims, characterized in that the valve (1, VTl) has at least one plate (3) in which the heat transfer duct (30, 36) is arranged. 7. The valve as claimed in claim 6, characterized in that the plate (3) has reinforcing devices (37) and/or cavities (38) in order to save weight. 8. The valve as claimed in claim 6 or 7, characterized in that the plate (3) is connected to a valve housing (7) in a materially joined and/or positively locking fashion. 9. The valve as claimed in claim 8, characterized in that the plate (3) is embodied in one piece with the valve housing (7). 10. The valve as claimed in one of claims 6 to 9, characterized in that the plate (3) has at least a first flange face (39, 40) for fastening purposes. 11. The valve as claimed in one of the preceding claims, characterized in that at least one aperture (41) for preventing a flow around the heat transfer duct (30, 36) is arranged in the heat transfer duct (30, 36). 12. The valve as claimed in one of the preceding claims, characterized in that the valve (1, VTl) has at least one sealing element (60), in particular a flat seal. 13. The heat exchanger for cooling an exhaust gas having at least one valve (1, VTl) as claimed in one of claims 1 to 12. 14. The heat exchanger as claimed in claim 13, characterized in that the heat exchanger {2, AGK) has a first flow duct through which the first medium (Ml) and/or a second medium (M2) can flow. 15. The heat exchanger as claimed in claim 13 or 14, characterized in that the heat exchanger (2, AGK) has a second flow duct through which a, third medium (M3) can flow. The heat exchanger as claimed in claim 14 or 15, characterized in that the second medium (M2) is a cooling fluid or air and/or the third medium (M3) is exhaust gas. 17. The heat exchanger as claimed in one of claims 13 to 16, characterized in that the heat exchanger (2, AGK) has an inlet diffuser (6) for the third medium (M3) . 18. The heat exchanger as claimed in claim 17, characterized in that the inlet diffuser (6) has a second flange face which can be connected to the first flange face (40) of the valve (1, VTl). 19. The heat exchanger as claimed in claim 18, characterized in that the sealing element (50) for sealing the valve (1, VTl) with respect to the inlet diffuser (6) is arranged between the first flange face (40) and the second flange face. 20. The heat exchanger as claimed in one of claims 13 to 19, characterized in that the heat exchanger (2, AGK) has at least one bypass valve (14) to permit the third medium (M3) to bypass the heat exchanger (2, AGK). 21. The heat exchanger as claimed in claim 20, characterized in that the at least one bypass valve (14) can be activated by means of a second actuator (15) . 22. The heat exchanger as claimed in one of claims 20 or 21, characterized in that the at least one bypass valve (14) and/or the valve (1, VTl) are arranged in, or adjacent to, the inlet diffuser (6). 23. A system having at least one valve (1, VTl) as claimed in one of claims 1 to 12 and having at least 'one heat exchanger (2, AGK) as claimed in one of claims 13 to 22, having at least one internal combustion engine (M) for a vehicle, at least a first turbine (Tl) of an exhaust gas turbosupercharger, wherein the valve is arranged on the inflow side of the heat exchanger (2, AGK), and the heat exchanger (2, AGK) is arranged on the high pressure side of the first turbine (Tl). 24. The system having at least one valve (1, VTl) as claimed in one of claims 1 to 12 and having at least one heat exchanger (2, AGK) as claimed in one of claims 13 to 22, having at least one internal combustion engine (M) for a vehicle, at least a first turbine (Tl) of an exhaust gas turbosupercharger, wherein the valve (1, VTl) is arranged on the inflow side of the heat exchanger (2, AGK), and the heat exchanger (2, AGK) is arranged on the low pressure side of the first turbine (Tl) . 25. The system as claimed in claim 23 or 24, characterized in that the system has at least a second heat exchanger (LLKl, LLK2) for cooling charge air and/or the first turbine (Tl) has a first compressor (VI) for supercharging charge air. 26. The system as claimed in one of claims 23 to 25, characterized in that the system has at least a second turbine (T2) which drives at least a second compressor (V2) for supercharging charge air.

Full Text

Valve for regulating an exhaust gas flow of an internal
combustion engine, heat exchanger for exhaust gas cooling, system having at least one valve and having at
least one heat exchanger
The present invention relates to a valve for regulating an exhaust gas flow of an internal combustion engine according to' the preamble of claim 1 and to a heat exchanger for cooling exhaust gas having at least one valve, and a system having at least one valve and having at least one heat exchanger.
In order to meet the current and future exhaust gas emission regulations, cooled exhaust gas recirculation is being used in diesel engines and/or spark ignition engines for passenger cars or for utility vehicles as a means of reducing the nitrogen oxide emissions (NOx) . Reliability problems of these systems are caused, for example, by failures or faults in a EGR valve which are due to the thermal loading by the hot exhaust gas stream or the formation of deposits from the exhaust gas stream. An EGR valve controls, in particular, the mass flow of recirculated exhaust gas which can flow through a heat exchanger, in particular an exhaust gas heat exchanger. The EGR valve can usually be actuated or activated electrically or pneumatically. The EGR valve can have various open-loop or closed-loop control positions. In a first position, the EGR valve prevents, for example, exhaust gas from flowing through the exhaust gas heat exchanger. In a second position, for example the entire mass flow of recirculated exhaust gas flows through the exhaust gas heat exchanger. In a third position of the EGR valve, a mass flow of recirculated gas flows through the exhaust gas heat exchanger, said mass flow being between zero mass flow of recirculated gas and the maximum mass flow of recirculated gas.

The EGR valve can be arranged downstream or upstream of the heat exchanger, in particular of the exhaust gas cooler. In addition, the EGR valve can be arranged in, or adjacent to, the exhaust gas cooler. In a further embodiment, the EGR valve can be embodied in one piece with the heat exchanger, in particular the exhaust gas cooler.
The EGR valve and the heat exchanger, in particular the exhaust gas cooler, can be arranged in a system having at least one internal combustion engine and at least one turbine, with which, in particular, a compressor for supercharging charge air or charge air and exhaust gas can be driven, on the outflow side of the turbine, i.e. on the low pressure side, or on the inflow side of the turbine, i.e. on the high pressure side.
When the EGR valve is arranged on the inflow side of the heat exchanger, in particular of the exhaust gas cooler, the EGR valve is subjected to high temperature requirements owing to the hot exhaust gas. It is known in this context that the temperature requirement of the EGR valve can be reduced if the exhaust gas is not fed directly to the EGR valve from the exhaust section but instead the recirculated exhaust gas is not fed to the EGR valve and/or the exhaust gas heat exchanger until it has passed through the cylinder head of the engine. As a result of this routing of exhaust gas, heat is already extracted from the hot exhaust gas by the engine coolant before said hot exhaust gas is in contact with the EGR valve. Nevertheless, the EGR valve still experiences very high temperature loading.
The arrangement of the EGR valve downstream of the exhaust gas cooler is usually selected in order to reduce the temperature loading of the EGR valve and of the corresponding actuator, in particular of the electrical or pneumatic actuator. However, it is disadvantageous here that the unburnt hydrocarbons (HC)

which are contained in the exhaust gas form deposits on the EGR valve in conjunction with soot particles. As a result of the relatively low gas temperatures after the exhaust gas has flowed through the exhaust gas heat exchanger, the deposits which are formed in the EGR valve can be removed again only with difficulty since, for example, the deposits can only be burnt off with difficulty. The deposits cause the valve to become blocked due to sooting up or carbonizing and is therefore no longer functionally capable.
On the other hand, arranging the EGR valve on the inflow side of the exhaust gas cooler makes it possible, owing to the high exhaust gas temperatures upstream of the exhaust gas heat exchanger, to burn off the deposits which are formed, for example in relatively high-load operating states of the internal combustion engine. However, the high temperature loading of the EGR valve also leads to heavy loading of the actuator. Even after the recirculated exhaust gas cools in the cylinder head, the actuator and EGR valve are still heavily loaded by the engine coolant.
The applicant's unpublished document DE 102 005 029 322.0 discloses an EGR valve and an arrangement for recirculating and cooling exhaust gas of an internal combustion engine with an EGR valve. In one exemplary embodiment, the valve device is arranged here on the inflow side of a high temperature cooler, or in another exemplary embodiment the exhaust gas cooler is arranged on the outflow side.
In addition, in the applicant's document DE 102 005 048 911.7, which is also still unpublished, an arrangement is disclosed for recirculating and cooling exhaust gas of an internal combustion engine in which an EGR valve is arranged on the outflow side of an exhaust gas cooler. In the applicant's document DE 102 005 049 309.2, which is also still unpublished.

an EGR valve is disclosed, which has, in particular, an oxidation catalytic converter on the inflow side of an exhaust gas cooler.
In the applicant's unpublished document DE 102 005 044 088.6, it is disclosed that an EGR valve is integrated into the inlet diffuser of a heat exchanger, in particular of an exhaust gas heat exchanger.
The object of the present invention is to improve a valve of the type mentioned at the beginning.
The object is achieved by means of the features of claim 1.
Further advantageous refinements of the invention emerge from the subclaims and from the drawings.
A valve is proposed for regulating an exhaust gas flow of an internal combustion engine which has at least one closure element and at least one actuator for activating the closure element, wherein the valve has at least one heat transfer duct for cooling the valve, through which heat transfer duct at least one first medium can flow.
The at last one closure element can perform open-loop or closed-loop control on, in particular, a mass flow of a second medium such as, for example, exhaust gas. The closure element can be actuated by means of an actuator. The valve has at least one heat transfer duct for cooling the valve, through which heat transfer duct at least one medium, in particular coolant such as cooling fluid or air can flow or does flow.
In one advantageous development, the heat transfer duct is embodied as an annular duct. The first medium, in particular cooling fluid or air, can particularly

advantageously flow from an inlet opening to an outlet opening here.
In addition it is possible to provide that the heat transfer duct has at least one wall pairing whose walls are embodied concentrically with respect to one another. In this way, the flow duct can particularly advantageously be formed in a plate by means of primary shaping fabrication methods such as, for example, injection molding, or by means of a material-removing fabrication method such as, for example, milling.
In one advantageous development, the valve has at least a first opening for the inflow of the first medium and/or at least a second opening for the outflow of the first medium. In this way, the first medium can particularly advantageously flow through the heat transfer duct via the first opening, and the first medium can particularly advantageously flow out again from the second opening after it has flowed through the heat transfer duct.
In addition it is possible to provide that the first medium is coolant, in particular a cooling fluid or air. In this way, the valve can be cooled particularly advantageously.
Furthermore, it can particularly preferably be provided that the valve has at least one plate in which the heat transfer duct is arranged. In this way, the heat transfer duct can particularly advantageously be provided in the plate, for example by means of a primary shaping fabrication method such as injection molding, or by means of a material-removing fabrication method such as milling or drilling, and can particularly advantageously be connected to the valve.
In a further advantageous embodiment, the plate has reinforcing devices and/or cavities in order to save

weight. In this way, the plate can be made particularly lightweight.
In addition it is possible to provide that the plate is connected to a valve housing in a materially joined and/or positively locking fashion. In this way, the plate can particularly advantageously be connected to the valve housing, for example by soldering, welding, bonding etc. and/or particularly advantageously connected in a positively locking fashion.
In a further advantageous development, the plate is embodied in one piece with the valve housing. In this way, it is possible, in particularly advantageous way, to make savings in terms of assembly processes.
In addition it is possible to provide that the plate has at least a first flange face for fastening purposes. It is particularly advantageously possible to fasten other components, for example an inlet diffuser and so on, to this flange face.
A further advantageous refinement is characterized in that at least one aperture for preventing a flow around the heat transfer duct is arranged in the heat transfer duct. This can particularly advantageously prevent first medium, such as for example coolant or air, from flowing from the first opening, in particular the inlet opening, directly to the second opening, in particular to the outlet opening, and in the process not flowing through the heat transfer duct, as a result of which the valve element would not be correspondingly cooled.
Furthermore, it can particularly preferably be provided that the valve has at least one sealing element, in particular a flat seal. This can particularly advantageously prevent media, such as for example the first medium, from escaping from the valve and/or other media entering the valve.

According to the invention, a heat exchanger for cooling exhaust gas having at least one valve as claimed in one of claims 1 to 12 is also proposed.
In one particularly preferred embodiment, the heat exchanger has a first flow duct through which the first medium and/or a second medium can flow. In this way, the first medium, which has in particular previously flowed through the valve, can particularly advantageously be made to flow through the heat exchanger, and/or a second medium can particularly advantageously be made to flow through the heat exchanger.
Furthermore, it can particularly advantageously be provided that the heat exchanger has a second flow duct through which a third medium can flow. In this way, the third medium, such as for example exhaust gas, can particularly advantageously be made to flow through the heat exchanger, in particular, the exhaust gas heat exchanger.
In addition, it is possible to provide that the second medium is a cooling fluid or air and/or the third medium is exhaust gas. In this way, the third medium, in particular exhaust gas, can be particularly advantageously cooled by the second medium, in particular the cooling fluid or the air.
In one advantageous development, the heat exchanger has an inlet diffuser for the third medium. In this way, the third medium can in particular advantageously be made to flow through the heat exchanger via the inlet diffuser.
In addition, it is possible to provide that the inlet diffuser has a second flange face which can be connected to the first flange face of the valve. In

this way, the valve can particularly advantageously be connected to the heat exchanger.
Furthermore, it can particularly preferably be provided that the sealing element for sealing the valve with respect to the inlet diffuser is arranged between the first flange face and the second flange face. In this way, the valve can particularly advantageously be sealed with respect to the inlet diffuser, and the inlet diffuser can particularly advantageously be sealed with respect to the sealing element.
In a further advantageous refinement, the heat exchanger has at least one bypass valve to permit the third medium to bypass the heat exchanger. In this way, a third medium such as, for example, exhaust gas, can particularly advantageously not be directed through the heat exchanger, in particular the exhaust gas heat exchanger, but rather can be directed around it with the result that, particularly advantageously, it is possible to avoid cooling the exhaust gas.
A further advantageous embodiment is characterized in that the at least one bypass valve can be activated by means of a second actuator. In this way, the bypass valve can particularly advantageously be activated by an electrical or pneumatic or hydraulic actuator.
In addition it is possible to provide that the at least one bypass valve and/or the valve are arranged in, or adjacent to, the inlet diffuser. In this way, there can particularly advantageously be a saving in terms of installation space.
According to the invention, in addition, a system having at least one valve as claimed in one of claims 1 to 12, and having at least one heat exchanger as claimed in one of claims 13 to 22, is proposed, which system has at least one internal combustion engine for

' ' a vehicle and at least a first turbine of an exhaust gas turbosupercharger, wherein the valve- is arranged on the inflow side of the heat exchanger and the heat exchanger is arranged on the high pressure side of the first turbine. In this way, the at least one heat exchanger, in particular the exhaust gas heat exchanger, and the valve can particularly advantageously be arranged on the high pressure side, with the result that the recirculation of exhaust gas can particularly advantageously take place on the high pressure side.
According to the invention, in addition, a further system having at least one valve as claimed in one of claims 1 to 12 and having at least one heat exchanger as claimed in one of claims 13 to 22 is proposed, said valve having at least one internal combustion engine for a vehicle and at least a first turbine of an exhaust gas turbocharger, wherein the valve is arranged on the inflow side of the heat exchanger and the heat exchanger is arranged on the low pressure side of the first turbine. In this way, the at least one heat exchanger, in particular the exhaust gas heat exchanger, and the valve can particularly advantageously be arranged on the low pressure side of the turbine, with the result that the exhaust gas can particularly advantageously be cooled on the low pressure side.
Furthermore, it can particularly preferably be provided that the system has at least a second heat exchanger for cooling charge air and/or the first turbine drives a compressor for supercharging charge air. In this way, the charge air in the second heat exchanger can particularly advantageously be cooled and/or the charge air can particularly advantageously be compressed by means of the compressor.

In addition, it is possible to provide that the system has at least a second turbine which drives at least a second compressor for supercharging charge air. In this way, the charge air and/or the recirculated exhaust gas can particularly advantageously be supercharged or compressed in two stages.
Further advantageous refinements of the invention emerge from the subclaims and from the drawings. The subject matters of the subclaims relate both to the valve according to the invention for controlling an exhaust gas flow of an internal combustion engine and to the heat exchanger according to the invention for cooling the exhaust gas having at least one valve, and to the system according to the invention having at least one valve and having at least one heat exchanger.
Exemplary embodiments of the invention are illustrated in the drawings and will be explained in more detail below, whereby this is not intended to restrict the invention. In said drawings
figure 1 is an isometric illustration of an exhaust gas heat exchanger with a coolable valve and a bypass valve,
figure 2 is an isometric sectional illustration of a coolable plate of a valve,
figure 3 is an isometric illustration of a coolable plate of a valve,
figure 4 is an isometric illustration of a coolable plate of a valve having a sealing element,
figure 5 is an isometric illustration of the bypass valve having an actuator,

figure 6 is a sectionai liiustration A-A tnrougn tne bypass valve,
figure 7 is a schematic illustration of a system having an exhaust gas heat exchanger and a coolable valve on the high pressure side with single-stage supercharging,
figure 8 is a schematic illustration of a valve having an exhaust gas heat exchanger and a coolable valve on the high pressure side with two-stage supercharging,
figure 9 is a schematic illustration of a system having an exhaust gas heat exchanger and a coolable valve on the low pressure side with single-stage supercharging, and
figure 10 is a schematic illustration of a system having an exhaust gas heat exchanger and a coolable valve on the low pressure side with two-stage supercharging.
The features of the various embodiments can be combined with one another as desired. The invention can also be used for fields other than those shown.
Figure 1 is an isometric illustration of an exhaust gas heat exchanger 2 having a coolable valve 1 and a bypass valve 14.
The valve 1 has at least one valve housing 7 and at least one plate 3, in particular cooling plate 3. The valve housing 7 has a valve housing flange 8, which is embodied essentially as a rectangular plate. In the illustrated exemplary embodiment, the corners of the plate are rounded, and in each case a valve housing flange bore 9 is provided adjacent to the corners (not denoted in more detail) of the valve housing flange 8.

in the illustrated exemplary embodiment, four valve housing flange bores 9 are provided in the valve housing flange 8. In another exemplary embodiment, one to four or more than four valve housing flange bores 9 are provided in the valve housing flange. The valve housing flange bore can be embodied here as a cylindrical bore or a stepped bore or as a right-parallelepiped-shaped opening or as an oval or cylindrical bore or as a bore formed from a combination of the previously mentioned shapes. In another exemplary embodiment, the valve housing flange 8 is embodied as a round, in particular circular or oval plate, or for example as a star-shaped plate. The valve housing flange 8 can also be embodied as a plate which can be a combination of polygonal, square or rectangular and/or round or oval shapes.
In the illustrated exemplary embodiment, the valve housing 7 is formed from the valve housing flange 8. The valve housing 7 is embodied essentially as a cylindrical section face from which a number of further cylindrical section faces and cylinders of different shapes and sizes are formed at different locations. In addition, a valve housing connecting flange 10 is formed from the valve housing 7. The valve housing connecting flange has a valve housing connecting flange opening 13. The valve housing connecting flange opening 13 is embodied essentially as a rectangular face with adjoining circular segments. In another exemplary embodiment, the valve housing connecting flange opening 13 can be embodied as a rectangular or square and/or circular or circular-segment-shaped and/or ellipsoidal opening. The valve housing connecting flange 10 has a frame (not denoted in more detail) , in which case, in the illustrated exemplary embodiment, the frame is a frame with circular segments or arc-shaped segments. In another exemplary embodiment, the frame (not denoted in more detail) can be rectangular or formed from rectangular elements and arcuate elements. In the

illustrated exemplary embodiment, cylinder sections, which each have a valve housing connecting flange bore 12, are formed from the frame. For example, connecting elements, such as screws, can be plugged through the valve housing connecting flange bores 12. Other elements, for example an actuator or other valve elements, can be connected to the valve housing at the valve housing connecting flange 10 in a positively locking fashion, for example by screwing and/or in a materially joined fashion, for example by soldering, welding, bonding etc.
In the illustrated exemplary embodiment, the valve housing connecting flange 10 has four valve housing connecting flange bores 12. In another exemplary embodiment, the valve housing connecting flange 10 has one to four or more than four valve housing connecting flange bores 12.
Valve housing fastening eyelets 11 are formed from the valve housing 7. In the illustrated exemplary embodiment, three valve housing fastening eyelets 11 are formed from the valve housing 7. In another exemplary embodiment, one to three or more than three valve housing fastening eyelets can be formed from the valve housing 7. In the illustrated exemplary embodiment, the valve housing fastening eyelets 11 can be formed in one piece with the valve housing 7. Likewise, the valve housing connecting flange 10 and/or the valve housing flange 8 can be embodied in one piece with the valve housing 7 in the illustrated exemplary embodiment.
In another exemplary embodiment, the valve housing flange 8 and/or the valve housing connecting flange 10 and/or the valve housing fastening eyelets 11 can be connected to the valve housing 7 in a materially joined fashion, for example by welding, soldering, bonding etc. In the illustrated exemplary embodiment, the valve

housing and/or the valve housing flange 8 and/or the valve housing connecting flange 10 and/or the valve housing fastening eyelets 11 are manufactured by means of a primary shaping fabrication method such as, for example, injection molding.
In another exemplary embodiment, the valve housing 7 and/or the valve housing flange 8 and/or the valve housing connecting flange 10 and/or the valve housing fastening eyelets 11 are formed by means of a material-removing fabrication method such as, for example, milling or turning or drilling. The valve housing 7 and/or the valve housing flange 8 and/or the valve housing connecting flange 10 and/or the valve housing fastening eyelets 11 can be formed from metal such as, for example, from steel, stainless steel or aluminum or from some other metal or from ceramic or from plastic or from a fiber composite material. The valve housing flange 8 is connected to the plate 3, in particular to the cooling plate 3 in a positively locking fashion, for example by screwing and/or in a materially joined fashion, for example by means of soldering, welding, bonding etc. The plate 3, in particular cooling plate 3, is arranged essentially parallel to the valve housing flange 8. In the illustrated exemplary embodiment, the plate 3 is embodied as a rectangular plate with rounded corners, in particular with four corners (not denoted in more detail). However, the plate 3 can also be embodied as a circular or cylindrical and/or oval element and/or from a combination of rectangular and cylindrical and/or oval or round elements. The inflow 4 is embodied as a cylindrical pipe in the illustrated exemplary embodiment.
In another exemplary embodiment, the inflow 4 can be embodied as a pipe with a square or rectangular or polygonal cross section.

In the illustrated exemplary embodiment, the inflow 4 is embodied in one piece with the plate 3. In another exemplary embodiment, the inflow 4 can be connected to the plate 3 in a materially joined fashion, for example by welding, soldering, bonding etc. and/or in a positively locking fashion. The outflow 5 is embodied essentially as a pipe.
In the illustrated exemplary embodiment, the pipe has a circular cross section. In another exemplary embodiment, the pipe can have a rectangular or square or polygonal cross section or a cross section composed of rectangular and round and/or oval elements. In the illustrated exemplary embodiment, the outflow 5 is embodied in one piece with the plate 3. In another exemplary embodiment, the outflow 5 can be connected to the plate 3 in a materially joined fashion, for example by soldering, welding, bonding etc., and/or in a positively locking fashion. In the illustrated exemplary embodiment, the outflow 5 is connected to the cooling medium inlet 20 of the heat exchanger 2, in particular of the exhaust gas heat exchanger. In another exemplary embodiment, the outflow 5 is not connected to the heat exchanger 2, in particular to the exhaust gas heat exchanger. Therefore, on the one hand, the valve housing flange 8 of the valve housing 7 is arranged adjacent to the plate 3. On the other side lying opposite, an inlet diffuser 6 for the inflow of the third medium, in particular of the exhaust gas, into the heat exchanger 2, in particular into the exhaust gas heat exchanger, is arranged adjacent to the plate 3. The inlet diffuser is fluidically connected to a heat exchanger inlet diffuser flange 23. In the illustrated exemplary embodiment, the heat exchanger inlet diffuser flange 23 is embodied in one piece with the inlet diffuser 5. In another exemplary embodiment, the heat exchanger inlet diffuser flange 23 is connected to the inlet diffuser 6 in a materially

joined fashion, for example by welding, soldering, bonding etc., and/or in a positively locking fashion.
The heat exchanger inlet diffuser flange 23 is embodied in the illustrated exemplary embodiment as a parallelogram-shaped plate with an inlet opening (not illustrated). The corners of the parallelogram are essentially rounded. The inlet diffuser 6 is embodied in the illustrated exemplary embodiment from stainless steel or from some other steel. In another exemplary embodiment, the inlet diffuser 6 can be embodied from a metal with a low density, for example from aluminum or from ceramic or from an, in particular, heat-resistant plastic or from a fiber composite material.
In the illustrated exemplary embodiment, the inlet diffuser 6 is embodied as a square with at least one cavity in the interior and with at least one opening (not illustrated) for the inflow of the third medium, in particular the exhaust gas. In another exemplary embodiment, the inlet diffuser is embodied, for example, as a pyramid, in particular as a four-sided or three-sided pyramid. In another further exemplary embodiment, the inlet diffuser 6 can be embodied as a cylinder with a circular or ellipsoidal cross-sectional area. In another exemplary embodiment, the inlet diffuser can be embodied from right-parallelepiped-shaped and/or cylinder-shaped elements and/or pyramid elements.
The plate 3, in particular the cooling plate, is constructed from steel, in particular from stainless steel, in the illustrated exemplary embodiment. In another exemplary embodiment, the plate 3 can be constructed from ceramic or from a heat-resistant plastic or from a fiber composite material or from a metal with a low density such as, for example, from aluminum.

The heat exchanger 2 is, in particular, an exhaust gas heat exchanger. In another exemplary embodiment, the heat exchanger 2 can be a coolant cooler and/or an oil cooler and/or a charge air cooler and/or a condenser for an air conditioning system and/or a gas cooler for an air conditioning system and/or a vaporizer for an air conditioning system.
In the illustrated exemplary embodiment, the heat exchanger 2, in particular the exhaust gas heat exchanger, is constructed from metal, for example from a steel, in particular from stainless steel, and/or from a metal with a low density, for example from aluminum and/or from a plastic, in particular from a heat-resistant plastic, and/or from ceramic and/or from a fiber composite material.
The heat exchanger 2, in particular the exhaust gas heat exchanger, has at least one heat exchanger housing 19. In the illustrated exemplary embodiment, the heat exchanger housing 19 is formed from a first right parallelepiped. The right parallelepiped has essentially a square cross-sectional area. On the two sides of the right parallelepiped which lie opposite one another, in each case a further right parallelepiped with a larger cross-sectional area than that of the first right parallelepiped which is located in the center between the two outer right parallelepipeds is formed from said right parallelepiped. The junction between the first right parallelepiped which is located in the center and the respectively adjoining outer right parallelepiped is embodied as a round junction. In another exemplary embodiment, this junction can also be constructed in a polygonal fashion such as for example as a shoulder. In the illustrated exemplary embodiment, the first right parallelepiped and the outwardly adjoining further right parallelepipeds are embodied in one piece. In another exemplary embodiment, the respectively

outwardly adjoining right parallelepipeds can be connected in a positively locking and/or materially joined fashion, in particular by welding, soldering, bonding etc.
In another exemplary embodiment, the heat exchanger housing 19 is composed as a cylinder or from a plurality of cylinder elements. In addition, in another embodiment the heat exchanger housing 19 can be embodied as a pyramid shape such as, for example, a three-sided or a four-sided or a multi-sided pyramid. In addition, in a further embodiment, the heat exchanger housing 19 can be constructed from conical segments or frustum-shaped segments. In a further embodiment, the heat exchanger housing 19 can be constructed from right-parallelepiped elements and/or pyramid elements and/or cylinder elements and/or conical elements or frustum elements.
The heat exchanger 2, in particular the exhaust gas heat exchanger, has in its interior a number of pipes, in particular a number of flat pipes, through which the third medium, in particular the exhaust gas, flows and which are connected to an at least first base, in particular to two bases (not illustrated). The connection is positively locking, in particular by crimping or folding or chamfering and/or in a materially joined fashion, for example by welding, soldering, bonding etc. In the illustrated exemplary embodiment, the pipes (not illustrated), in particular flat pipes, are constructed from metal such as, for example, from steel, in particular from stainless steel, or from another material such as, for example, a metal with a low density such as aluminum, or from a fiber composite material or from a heat-resistant plastic. The flat pipes have a plurality of turbulence-generating elements such as, for example, winglets or other punched-out elements. These turbulence-generating elements may be produced, for example, in the flat

pipes by means of a shaping fabrication method such as, for example, punching, stamping, pressing etc., or by a primary shaping fabrication method. In addition, turbulence inserts such as, for example, turbulence plates can also be provided in the flat tubes or between flat tubes.
The tube plates (not denoted) are connected to the heat exchanger housing 19 by positive locking such as, for example, folding, beading, crimping etc. and/or in a materially joined fashion by, for example, welding, soldering, bonding etc. In another exemplary embodiment, the third medium, in particular the exhaust gas, flows between plates which can be stacked one on top of the other or are stacked one on top of the other. Between these plates it is possible to insert, for example, turbulence-generating elements such as turbulence plates which cause eddying of the flow and therefore lead to a better transfer of heat or a better transmission of heat. The plates can be connected to one another, for example, in a materially joined fashion by welding, soldering, bonding etc. and/or in a positively locking fashion by crimping or folding.
At least one bypass valve 14 is arranged adjacent to the heat exchanger 2 and/or adjacent to the valve 1 and/or adjacent to the inlet diffuser 6.
The bypass valve 14 has a valve element (not illustrated) which can be activated or is activated by means of a bypass valve actuator 15. The bypass valve element is adjusted between a plurality of positions or can assume a plurality of positions by means of a bypass valve lifting device 17 which can be activated or is activated by means of a bypass valve actuator 15. The bypass valve lifting device 17 has at least one bypass valve spring element 16. In the illustrated exemplary embodiment, the bypass valve spring element 16 is embodied as a helical spring. In another

exemplary embodiment, the bypass valve spring element 16 can be embodied as a different spring element, for example as a leaf spring element etc.
In the illustrated exemplary embodiment, the bypass valve 14 is integrated into the inlet diffuser 6 and/or into the heat exchanger 2, in particular into the exhaust gas heat exchanger. In another exemplary embodiment, the bypass valve 14 can be embodied as an independent add-on and is adjacent to the heat exchanger 2 and/or to the inlet diffuser 6 and/or can be connected to the heat exchanger 2, in particular to the exhaust gas heat exchanger and/or to the inlet diffuser 6 in a materially joined fashion, for example by welding, soldering, bonding etc. and/or in a positively locking fashion.
In the illustrated exemplary embodiment, the heat exchanger 2, in particular the exhaust gas heat exchanger, has a coolant inlet 20 in one of the outer right parallelepipeds. Cooling medium, such as for example coolant, in particular aqueous coolant, or air, can flow into the heat exchanger 2 through this cooling medium inlet 20 and can flow through this heat exchanger 2, in particular the exhaust gas heat exchanger, and in the process cool the third medium, in particular the exhaust gas. The second medium, in particular the cooling medium, in particular the aqueous cooling medium or the air, flow around the flat pipes or the plates between which the third medium, in particular the exhaust gas, flows. The second medium, in particular the cooling medium flows in at least one flow duct (not illustrated) between the heat exchanger housing 19, in particular the heat exchanger housing wall, and the flat pipes or the plates. Turbulence-generating elements such as, for example, punched-out elements, knobs, winglets or turbulence plates, which are provided improve the transfer of heat in this context. The second medium, in particular the coolant.

leaves the heat exchanger 2, in particular the exhaust gas heat exchanger, through an outlet opening (not illustrated) which is located on the underside of the heat exchanger housing 19, which underside cannot be seen in figure 1. In the illustrated exemplary embodiment, the cooling medium exits from the outer right parallelepiped which is located adjacent to the heat exchanger outlet diffuser 21. In another exemplary embodiment, the coolant inlet 20 is arranged on any desired side of the outer right parallelepiped or of the inner right parallelepiped. Likewise, in another exemplary embodiment, the first or second medium, in particular the cooling medium, flows out at any desired location on any desired side of one of the outer right parallelepipeds or at any desired location on any desired side of the inner right parallelepiped. In the illustrated exemplary embodiment, the outflow 5 of the first medium, in particular of the cooling medium, in particular of the aqueous cooling fluid or the air, is connected to the cooling medium inlet 20 of the heat exchanger 2, in particular of the exhaust gas heat exchanger. In another exemplary embodiment, the outflow 5 is not connected to the cooling medium inlet 20. In the illustrated exemplary embodiment, the third medium, the exhaust gas, which flows through the heat exchanger 2, is cooled by the first medium Ml, in particular the cooling medium, in particular the aqueous cooling fluid or air, and after the first medium Ml flows into the plate 3 via the inflow 4 it flows through the plate 3 and leaves the plate 3 via the outflow 5, flows through the pipe and the pipe bend into the cooling medium inlet 20 of the heat exchanger 2, in particular the exhaust gas heat exchanger, flows through it and in the process cools the third medium, in particular the exhaust gas, and leaves the heat exchanger 2, in particular the exhaust gas heat exchanger, again from the cooling medium outlet (not illustrated). The cooling medium 1 can subsequently be cooled, for example, by a coolant cooler and subsequently fed back

again to the inflow 4 of the plate 3, in particular of the cooling plate 3.
Figure 2 shows an isometric sectional illustration of a coolable plate 3 of a valve 1. Identical features are provided with the same reference symbols as in figure 1.
In the illustrated exemplary embodiment, the plate 3, in particular the cooling plate, is embodied from a metal, for example stainless steel or from some other steel. In another exemplary embodiment, the plate 3 can be constructed from a metal with a low density such as, for example from aluminum or from a heat-resistant plastic or from ceramic or from a fiber composite material,
The plate 3 is used to cool the valve 1 and/or a bypass plate (not illustrated) and its bypass plate actuator.
Plate 3 has a plate outer wall 43 which is embodied, in particular, in a circumferential fashion. In the illustrated exemplary embodiment, the plate 3 is embodied as a pentagonal plate whose corners are rounded. In another exemplary embodiment, the plate 3 has sharp corners. In another exemplary embodiment, the plate 3 has a triangular, quadrilateral or polygonal shape. In another exemplary embodiment, the plate has a polygonal and/or round and/or oval cross-sectional area. The plate 3 can be manufactured by means of a primary shaping fabrication method such as, for example, injection molding, in particular metal injection molding, or by means of a material-removing fabrication method, in which case, in particular, cutouts and/or cavities and/or bores can be provided in the plate by means of a material-removing fabrication method such as, for example, drilling, milling, eroding etc.

In the illustrated exemplary embodiment, the plate outer wall 43 is embodied essentially as a frame element. In this frame, the plate 3 has a wall pairing 31 which has at least a first plate wall 32 and a further second plate wall 33. The first plate wall 32 is embodied in the illustrated exemplary embodiment as a cylinder section which has a round cross-sectional area. The second plate wall 33 is also embodied in the illustrated exemplary embodiment as a cylinder section with a circular cross-sectional area. The first plate wall 32 has a larger cross-sectional diameter than the second plate wall 33. The annular duct 30 is formed between the first plate wall 32 and the second plate wall 33. The annular duct 30 is one possible embodiment of the heat transfer duct 36. In another exemplary embodiment, the heat transfer duct 36 can be embodied as a rectangular duct or as duct with a star shape or as a duct with a combination of arcuate and rectangular sections. The heat transfer duct 36 or the annular duct 30 is bounded in the plane of the first flange area 40 by the first heat transfer duct floor 45.
The second plate wall 33 encloses a plate bore 44. The plate bore 44 is embodied in the illustrated exemplary embodiment as a through-bore. In another exemplary embodiment, the plate bore 44 can have a round and/or elliptical and/or rectangular and/or polygonal cross section. In the illustrated exemplary embodiment, the first plate wall 32 is embodied, at least in certain sections, in one piece with the plate outer wall 43. The rounded corners of the plate outer wall 43 have hollow-cylindrical formations which have fastening bores 42. The fastening bores 42 can contain, for example, threads. However, they can also be formed as bores without a thread. In the illustrated exemplary embodiment, the plate 3 has four of these formations with, in each case, one fastening bore 42. In another exemplary embodiment, the plate 3 can have one to four or more than four hollow-cylindrical formations, each

with a fastening bore 42 or with more than one fastening bore 42. Reinforcing devices 37, which are embodied as reinforcement struts or reinforcing walls, extend from the plate outer wall 43 to the heat transfer duct 36 or to the annular duct 30. A plurality of these reinforcing devices 37 intersect here, extend at different angles with respect to one another and therefore reinforce the plate 3. The reinforcing devices 37 and/or the plate outer wall 43 enclose cavities 38 which have the purpose of reducing the weight of the plate 3. These cavities 38 can be provided in the plate 3 by primary shaping fabrication methods, with which the plate 3 is manufactured, or by a material-removing fabrication method such as eroding and/or drilling and/or milling. In the illustrated exemplary embodiment, the plate outer wall 4 3 and/or the reinforcing devices 37 and/or the first plate wall 32 and/or the second plate wall 33 and/or the aperture 41 and/or the inflow 4 and/or the outflow 5 can be embodied in one piece with the plate. In another exemplary embodiment, the elements which are mentioned in the previous sentence can, however, also be connected to the plate, for example by means of a materially joining method, such as for example soldering, welding, bonding etc. to the plate 3.
The first medium Ml, in particular the cooling medium such as, for example, the aqueous coolant or air, passes into the plate 3 or into the heat transfer duct 36 or into the annular duct 30. In the illustrated exemplary embodiment, the aperture 41 is embodied as two projections, each projecting from the inner side of the first plate wall 32 in to the heat transfer duct 36 or into the annular duct 30, and the second projection is embodied such that it projects from the inner side of the duct in the second plate wall 33 into the heat transfer duct 36 or into the annular duct 30. The aperture 41 prevents the first medium from flowing directly from the' inflow and back into the outflow 5

again without predominantly flowing through the entirety of the heat transfer duct 36. In another exemplary embodiment, the aperture 41 can also be embodied as a continuous wall. The first medium Ml flows, after entering via the first plate opening 34 into the heat transfer duct 36 or the annular duct 30, through the heat transfer duct 36 or the annular duct and leaves it via a second plate opening 35 in order to flow out of the plate 3 again via the outflow 5. The plate 3 has a first flange face 40 on its underside. Opposite the first flange face 40 and essentially parallel thereto the plate 3 has a third flange face 39.
The inflow 4 and/or the outflow 5 are embodied in the illustrated exemplary embodiment as a pipe with a round cross section. In another exemplary embodiment, the inflow 4 and/or the outflow 5 can be embodied as a pipe with an elliptical and/or rectangular and/or polygonal cross section.
The inflow 4 and the outflow 5 have an angle a. The angle a can assume values between 1° and 180°, in particular between 10° and 150°, in particular between 20° and 120°, in particular between 30° and 100°, in particular between 35° and 90°, in particular between 40° and 70°.
Figure 3 is an isometric illustration of a coolable plate 3 of a valve 1. Identical features have been provided with the same reference symbols as in the previous figures.
In contrast to figure 2, figure 3 also has the second heat transfer duct floor 50. The heat transfer duct 36 or the annular duct 30 is surrounded at least in certain sections, by the first plate wall 32 (not illustrated), the second plate wall 33, the first heat

transfer duct floor 45 (not illustrated) and the second heat transfer duct floor 50.
Figure 4 is an isometric illustration of a coolable plate 3 of a valve 1 with a sealing element 60. Identical features have been provided with the same reference symbols as in the previous figures.
In contrast to figure 3, figure 4 shows the plate 3, in particular the cooling plate, with a sealing element 60 which is arranged essentially parallel to and/or adjacent to the third flange face 39. The sealing element 60 is constructed from rubber or from some other plastic, in particular from an elastomer. The sealing element 60 is embodied as a flat seal in the illustrated exemplary embodiment. The sealing element 60 has first sealing bores 61 and second sealing bores 62. In the illustrated exemplary embodiment, the sealing element 60 has four second sealing bores 62 and two first sealing bores 61. In another exemplary embodiment (not illustrated) , the sealing element 60 may have one to four or more than four second sealing bores 62 and/or one to two or more than two first sealing bores 61. The first sealing bores 61 and the second sealing bores 62 are arranged essentially adjacent to the outer edge (not denoted) of the sealing element 60. In the illustrated exemplary embodiment, the sealing element 60 has an essentially rectangular face with rounded corners. In another exemplary embodiment, the sealing element 60 can have a round shape and/or a polygonal shape and/or an elliptical shape and/or a polygonal shape. In addition, the sealing element has a third sealing bore 63. The third sealing bore 63 has essentially the same diameter as the plate bore 44. The second sealing bore 62 has essentially the same diameter as the fastening bore 42. The diameter of the first sealing bore 61 is smaller than the diameter of the second sealing bore 62. In another exemplary embodiment, the first sealing bore 61

has a larger diameter than the second sealing bore 62. The third sealing bore 63 has a larger diameter than the first sealing bore 61 and/or the second sealing bore 62. In another exemplary embodiment, the third sealing bore can have a smaller diameter than the first sealing bore 61 and/or than the second sealing bore 62.
Figure 5 is an isometric illustration of a bypass valve 14 with a bypass valve actuator 15. Identical features have been provided with the same reference symbols as in the previous figures.
A heat exchanger housing section 70 of the heat exchanger 2, in particular of the exhaust gas heat exchanger, is embodied essentially as a right parallelepiped with rounded edges and an essentially square cross-sectional area. In another exemplary embodiment, the heat exchanger housing section 70 can have a rectangular and/or square and/or round and/or elliptical cross section.
A tube plate 71, which is embodied essentially from stainless steel or from some other metal such as, in particular, aluminum, or from a heat-resistant plastic or from ceramic or from a fiber composite material, has a bypass opening 72 which is embodied essentially as an elongated hole. This bypass opening 72 is separated from a number of tube plate openings 73 by a bypass valve dividing wall 76. The tube plate openings 73 are embodied essentially as an elongated hole and have a smaller cross section than the bypass opening 72. A plurality of tube plate openings 73 are arranged in a grid shape in a plurality of rows and columns. Flat tubes (not shown) are plugged in through the tube plate openings 73 and are connected to the tube plate in a positively locking fashion by, for example, folding, beading, crimping etc. and/or in a materially joined fashion by welding, soldering, bonding etc. The third medium, in particular exhaust gas M3, in particular

aqueous cooling fluid or air, flows to the bypass valve ■ element 75 in the direction of the arrow M3. The bypass valve element may assume various positions here. In a first position, the entire third medium M3 is fed through the tube plate opening 73, and the third medium M3 is not fed through the bypass opening 72. In a second position, third medium M3 is not fed through the tube plate openings 73 and the entirety of the third medium M3 is fed through the bypass opening 72. In a third position of the bypass valve element 75, third medium M3 is fed both through the tube plate openings 73 and through the bypass opening 72. In a fourth position of the bypass valve element 75, third medium M3 is neither fed through the bypass opening 72 nor through the tube plate openings 73.
The bypass valve element 75 is actuated or activated essentially by the bypass valve actuator 15. The bypass valve actuator 15 has, in the illustrated exemplary embodiment, a housing (not denoted in more detail) which is composed of cylinder segments which are, in particular, arranged concentrically. The bypass valve actuator 15 activates a bypass valve lifting device 17 which activates the bypass valve element 75 via a bypass valve spring element 16. The bypass valve spring element 16 ensures that, after actuation via the bypass valve actuator 15, the bypass valve element 75 is moved back into a specific position.
The heat exchanger housing section 70 has a coolant inlet 74 via which first medium, in particular coolant, such as, for example, aqueous cooling fluid or air or second medium, in particular aqueous cooling fluid or air, flow into the heat exchanger 2.
In this context, reference is made to the still unpublished document DE 102 005 044 088.6 by the applicant in which a device for controlling an exhaust gas flow is disclosed. This is to be considered as

constituting an express disclosure of the entire contents of the unpublished document DE 102 005 044 088.6 by the applicant.
Figure 6 is a sectional illustration A-A through the bypass valve 14. Identical features have been provided with the same reference symbols as in the previous figures.
The bypass valve 14 is arranged in a housing wall section 80. The housing wall section has a first stop 82 for the bypass valve element 81 and a second stop 83 for the bypass valve element 81. If the bypass valve element is located adjacent to the first stop 81 or if it is in contact, in particular, with the first stop 82, the third medium can flow into the bypass BP and not to the heat exchanger WT. If the bypass valve element 81 is arranged adjacent to the second stop 83, or the bypass valve element 81 is in contact with the second stop 83, at least in certain sections, the entirety of the third medium M3 flows to the heat exchanger, in particular the exhaust gas heat exchanger 2, and not to the bypass duct BP. If the bypass valve element 81 is in a position between the first stop 82 and the second stop 83, the third medium M3 flows both to the heat exchanger WT, in particular to the exhaust gas heat exchanger 2, and to the bypass duct BP.
Figure 7 is a schematic illustration of a system with an exhaust gas heat exchanger AGK and a coolable valve VPl on the high pressure side with single-stage supercharging. Identical features have been provided with the same reference symbols as in the previous figures.
The system illustrated in figure 7 shows an internal combustion engine M and a heat exchanger AGK, which corresponds to the heat exchanger 2, in particular the exhaust ga=; heat exchanaer. In addition, the system has

a valve VTl, which corresponds to the valve 1. Air which is sucked in from the outside, which is at the pressure NDl, the low pressure, is compressed, by means of a first compressor VI which is driven by means of a first turbine, to the relatively high pressure HD, the high pressure. The turbine Tl and the compressor VI are embodied as a turbocharger. The air which is compressed to the high pressure HD warms up and is cooled in the charge air cooler LLKl. The cooled charge air has recirculated and cooled exhaust gas fed to it and the mixture of charge air and exhaust gas is fed into the combustion engine M. Exhaust gas leaves the combustion engine M and some of the exhaust gas is fed to the first valve VTl, the valve 1, in particular the EGR valve, and subsequently cooled in the heat exchanger AGK, in particular the heat exchanger 2, in particular the exhaust gas heat exchanger, and added again to the compressed and cooled charge air. In figure 7, the supercharging of the charge air takes place in a single stage by means of the compressor VI and/or by means of the turbocharger.
Figure 8 is a schematic illustration of a system with an exhaust gas heat exchanger AGK and a coolable valve VTl on the high pressure side with two-stage supersupercharging. Identical features have been provided with the same reference symbols as in the previous figures.
In contrast to figure 8, the at the pressure level ND2 is compressed from the low pressure level to the low pressure level NDl by the compressor V2. The compressed air heats up during this and is cooled in the charge air cooler LLK2 and compressed by the compressor VI to the high pressure level HD. The compressor VI is driven by the first turbine Tl, which relaxes part of the exhaust gas from the high pressure level HD to the low pressure level NDl. In addition, the compressor V2 is driven by the second turbine T2, which relaxes part of

the exhaust gas from the low pressure level NDl to the low pressure level ND2. Both in figure 7 and in figure 8, the valve VTl, in particular valve 1, is arranged on the inflow side of the heat exchanger AGK, in particular of the exhaust gas heat exchanger 2. Both in figure 1 and in figure 8, the valve VTl is embodied as a separate structural unit upstream of the exhaust gas heat exchanger AGK, in particular the heat exchanger 2. In another exemplary embodiment, the valve VTl can be embodied in one piece with the exhaust gas heat exchanger AGK, or integrated into it.
In another exemplary embodiment, the valve 1, VTl, can also be arranged on the outflow side of the heat exchanger AGK, 2.
Figure 9 is a schematic illustration of a system with a heat exchanger AGK and a coolable valve VTl on the low pressure side with single-stage supersupercharging. Identical features have been provided with the same reference symbol as in the previous figures.
In contrast to figure 7, the coolable valve VTl, in particular the valve 1 and/or the heat exchanger AGK, in particular the exhaust gas heat exchanger 2, are arranged on the low pressure side, i.e. the outflow side of the first turbine Tl. In the illustrated exemplary embodiment, the valve VTl, in particular the valve 1, is arranged as a separate structural unit on the inflow side of the heat exchanger AGK, in particular of the exhaust gas heat exchanger 2. In another exemplary embodiment, the valve VTl is embodied in one piece with the heat exchanger AGK, in particular the exhaust gas heat exchanger 2, and/or integrated into it.
Figure 10 is a schematic illustration of a system with a heat exchanger AGK and a coolable valve VTl on the low pressure side with two-stage supersupercharging.

Identical features have been provided with the same reference symbols as in the previous figures.
In contrast to figure 9, the valve VTl and/or the heat exchanger AGK, in particular the exhaust gas heat exchanger 2, are arranged in the low pressure region ND2. The valve VTl, in particular the valve 1, is arranged on the outflow side of the second turbine T2, as is the exhaust gas heat exchanger AGK, in particular the exhaust gas heat exchanger 2, with the valve VTl being arranged as a separate structural unit on the inflow side of the heat exchanger AGK. In another exemplary embodiment, the valve VTl, in particular the valve 1, can be embodied in one piece with the heat exchanger AGK, in particular the exhaust gas heat exchanger 2, and/or integrated into it. Sucked-in air is mixed with the cooled, recirculated exhaust gas and compressed in the second compressor V2 to the low pressure level NDl and subsequently cooled in a second charge air cooler LLK2 and compressed in a first compressor VI to the high pressure level HD.
The valve 1, VTl, can be embodied as a slide valve, for example as in the unpublished document DE 102 005 041 149.5, the entire content of which is to be considered as having been disclosed herewith. In addition the valve 1, VTl, can be embodied as a valve, as is disclosed in the unpublished document DE 102 005 041 150.9 by the applicant, the entire content of which is to be considered as being expressly disclosed herewith.
The valve 1, VTl can also be embodied as a valve as is disclosed in the unpublished document DE 102 005 044 089.4 by the applicant, the entire content of which is to be considered as expressly disclosed herewith. In addition, the valve 1, VTl, can also be embodied as a valve such as is disclosed in the unpublished document DE 102 005 058 494.2 by the

applicant, the entire content of which is to be considered as expressly disclosed herewith.
The features of the various exemplary embodiments can be combined with one another as desired. The invention can also be used for fields other than those indicated.

WE CLAIM
1. A valve for regulating an exhaust gas flow of an
internal combustion engine, having at least one closure
element and at least one actuator for activating the
closure element, characterized in that the valve
(1, VTl) has at least one heat transfer duct (30, 36) for cooling the valve, through which heat transfer duct
(30, 36) at least one medium (Ml) can flow.
2. The valve as claimed in claim 1, characterized in that the heat transfer duct (36) is embodied as an annular duct (30).
3. The valve as claimed in one of the preceding claims, characterized in that the heat transfer duct (30, 36) has at least one wall pairing (31) whose walls (32, 33) are embodied concentrically with respect to one another.
4. The valve as claimed in one of the preceding claims, characterized in that the valve (1, VTl) has at least a first opening (34) for the inflow (4) of the first medium (Ml) and/or at least a second opening (35) for the outflow (5) of the first medium (Ml).
5. The valve as claimed in one of the preceding claims, characterized in that the first medium (Ml) is coolant, in particular a cooling fluid or air.
6. The valve as claimed in one of the preceding claims, characterized in that the valve (1, VTl) has at least one plate (3) in which the heat transfer duct (30, 36) is arranged.
7. The valve as claimed in claim 6, characterized in that the plate (3) has reinforcing devices (37) and/or cavities (38) in order to save weight.

8. The valve as claimed in claim 6 or 7, characterized in that the plate (3) is connected to a valve housing (7) in a materially joined and/or positively locking fashion.
9. The valve as claimed in claim 8, characterized in that the plate (3) is embodied in one piece with the valve housing (7).
10. The valve as claimed in one of claims 6 to 9, characterized in that the plate (3) has at least a first flange face (39, 40) for fastening purposes.
11. The valve as claimed in one of the preceding claims, characterized in that at least one aperture (41) for preventing a flow around the heat transfer duct (30, 36) is arranged in the heat transfer duct
(30, 36).
12. The valve as claimed in one of the preceding claims, characterized in that the valve (1, VTl) has at least one sealing element (60), in particular a flat seal.
13. The heat exchanger for cooling an exhaust gas having at least one valve (1, VTl) as claimed in one of claims 1 to 12.
14. The heat exchanger as claimed in claim 13, characterized in that the heat exchanger {2, AGK) has a first flow duct through which the first medium (Ml) and/or a second medium (M2) can flow.
15. The heat exchanger as claimed in claim 13 or 14, characterized in that the heat exchanger (2, AGK) has a second flow duct through which a, third medium (M3) can flow.

The heat exchanger as claimed in claim 14 or 15,
characterized in that the second medium (M2) is a
cooling fluid or air and/or the third medium (M3) is
exhaust gas.
17. The heat exchanger as claimed in one of claims 13 to 16, characterized in that the heat exchanger (2, AGK) has an inlet diffuser (6) for the third medium (M3) .
18. The heat exchanger as claimed in claim 17, characterized in that the inlet diffuser (6) has a second flange face which can be connected to the first flange face (40) of the valve (1, VTl).
19. The heat exchanger as claimed in claim 18, characterized in that the sealing element (50) for sealing the valve (1, VTl) with respect to the inlet diffuser (6) is arranged between the first flange face
(40) and the second flange face.
20. The heat exchanger as claimed in one of claims 13
to 19, characterized in that the heat exchanger
(2, AGK) has at least one bypass valve (14) to permit
the third medium (M3) to bypass the heat exchanger
(2, AGK).
21. The heat exchanger as claimed in claim 20,
characterized in that the at least one bypass valve
(14) can be activated by means of a second actuator
(15) .
22. The heat exchanger as claimed in one of claims 20 or 21, characterized in that the at least one bypass valve (14) and/or the valve (1, VTl) are arranged in, or adjacent to, the inlet diffuser (6).
23. A system having at least one valve (1, VTl) as claimed in one of claims 1 to 12 and having at least

'one heat exchanger (2, AGK) as claimed in one of claims 13 to 22, having
at least one internal combustion engine (M) for a vehicle,
at least a first turbine (Tl) of an exhaust gas turbosupercharger, wherein the valve is arranged on the inflow side of the heat exchanger (2, AGK), and the heat exchanger (2, AGK) is arranged on the high pressure side of the first turbine (Tl).
24. The system having at least one valve (1, VTl) as
claimed in one of claims 1 to 12 and having at least
one heat exchanger (2, AGK) as claimed in one of claims
13 to 22, having at least one internal combustion
engine (M) for a vehicle, at least a first turbine (Tl)
of an exhaust gas turbosupercharger, wherein the valve
(1, VTl) is arranged on the inflow side of the heat
exchanger (2, AGK), and the heat exchanger (2, AGK) is
arranged on the low pressure side of the first turbine
(Tl) .
25. The system as claimed in claim 23 or 24, characterized in that the system has at least a second heat exchanger (LLKl, LLK2) for cooling charge air and/or the first turbine (Tl) has a first compressor (VI) for supercharging charge air.
26. The system as claimed in one of claims 23 to 25, characterized in that the system has at least a second turbine (T2) which drives at least a second compressor (V2) for supercharging charge air.

Documents:

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Patent Number

272528

Indian Patent Application Number

4370/CHENP/2008

PG Journal Number

15/2016

Publication Date

08-Apr-2016

Grant Date

06-Apr-2016

Date of Filing

19-Aug-2008

Name of Patentee

BEHR GMBH & CO. KG

Applicant Address

MAUSERSTRASSE 3, 70469 STUTTGART,

Inventors:

#	Inventor's Name	Inventor's Address
1	CHRIST, MAREN,	SIEGFRIEDSTR. 73, 90461 NURNBERG
2	MULLER, ROLF,	HEINRICH-HEINE-STR. 5, 71642 LUDWIGSHAFEN,

PCT International Classification Number

F02M25/07

PCT International Application Number

PCT/EP07/01175

PCT International Filing date

2007-01-12

PCT Conventions:

#	PCT Application Number	Date of Convention	Priority Country
1	102006009151.5	2006-02-24	Germany