Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
  • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
  • F28D7/0066—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids
  • F28D7/0083—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids with units having particular arrangement relative to a supplementary heat exchange medium, e.g. with interleaved units or with adjacent units arranged in common flow of supplementary heat exchange medium
  • F28D7/0091—Multi-circuit heat-exchangers, e.g. integrating different heat exchange sections in the same unit or heat-exchangers for more than two fluids with units having particular arrangement relative to a supplementary heat exchange medium, e.g. with interleaved units or with adjacent units arranged in common flow of supplementary heat exchange medium the supplementary medium flowing in series through the units
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
  • F28D7/16—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation
  • F28D7/1684—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section
  • F28D7/1692—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged in parallel spaced relation the conduits having a non-circular cross-section with particular pattern of flow of the heat exchange media, e.g. change of flow direction
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
  • F28F9/02—Header boxes; End plates
  • F28F9/0219—Arrangements for sealing end plates into casing or header box; Header box sub-elements
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
  • F28F9/26—Arrangements for connecting different sections of heat-exchange elements, e.g. of radiators
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
  • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
  • F28D21/0001—Recuperative heat exchangers
  • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
  • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
  • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
  • F28F2009/224—Longitudinal partitions
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F9/00—Casings; Header boxes; Auxiliary supports for elements; Auxiliary members within casings
  • F28F9/22—Arrangements for directing heat-exchange media into successive compartments, e.g. arrangements of guide plates
  • F28F2009/222—Particular guide plates, baffles or deflectors, e.g. having particular orientation relative to an elongated casing or conduit
  • F28F2009/226—Transversal partitions

Definitions

• Heat exchanger exhaust gas recirculation system and use of a heat exchanger
• the invention relates to a heat exchanger for two-stage heat exchange between a first fluid on the one hand and a second and third fluid of different temperature on the other hand, comprising: a block for the separate and heat exchanging guidance of the first and the second and third fluid, comprising: a number of the first fluid flow-through flow channels, a first the flow channels receiving, of the second fluid can flow through the chamber of a high-temperature part, and a second flow channels receiving, of the third fluid flow-through chamber of a low-temperature part, and a housing in which the first and second chambers and the flow channels are arranged.
• the exhaust gas recirculation in particular the cooled exhaust gas recirculation is used in today's vehicles due to legal provisions to reduce particulate matter and pollutant, especially a nitrogen oxide (NO x ) - emission.
• EGR exhaust gas recirculation
• a portion of the exhaust gas is removed from the exhaust gas line at an appropriate point in an exhaust gas recirculation system, cooled and fed back to a motor on the fresh charge side.
• the lowering of an oxygen partial pressure associated with the EGR results in lower peak combustion temperatures, which in turn results in lower rates of formation of thermal NO x .
• the cooling of the recirculated exhaust gas additionally amplifies the effect.
• the said principle has proved to be particularly effective in the passenger car sector.
• An applicant's exhaust gas recirculation system is described in more detail, for example, in DE 60 024 390 T2 and shows a single-stage exhaust gas cooler which, with the aid of a coolant circuit coupled to the engine cooling water, adjusts the exhaust gas to discharge temperatures of up to 110 ° C., depending on the size of the exhaust gas cooler ° can cool down.
• a two-stage exhaust gas cooling system according to which a second low-temperature heat exchanger is arranged behind a first high-temperature heat exchanger, the latter being coupled to a high-temperature cooling circuit for recooling and the latter being coupled to a low-temperature cooling circuit.
• the low-temperature cooling circuit can have coolant inlet temperatures in the range of 40-60 C °.
• Embodiments of this type are known from the applicant, for example from DE10203003A1, in which a two-stage heat exchanger with a bypass channel is described in more detail.
• the accommodation of a block with a high-temperature part and a low-temperature part for heat exchange in a common housing has the advantage that comparatively few components are needed to realize a two-stage heat exchanger - on the other hand, this makes a comparatively improved separation of the high-temperature part and low-temperature part necessary.
• the separation quality between the high-temperature part and the low-temperature part of the two-stage heat exchanger should be adaptable.
• a separation between an oil-based and water-based coolant should be particularly good, while in the event that the second and third fluid is formed in the form of similar coolant leaks are generally tolerable, but kept as low as possible leakage rates between a high-temperature part and a low-temperature part should be.
• Object of the present invention is to provide a two-stage heat exchanger, which has a relatively simple design and yet has a demand-adapted and safe separation of a high-temperature part and low-temperature part. In any case, a possibly adjusted demand, leakage rate between a high-temperature part and a low-temperature part should be kept relatively low.
• the object is achieved by the invention with a heat exchanger of the type mentioned, in which according to the invention, the first chamber and the second chamber are separated by a separating surface, which is fixed in a groove.
• the separating surface can be formed in the form of an arbitrary planar arrangement.
• the separating surface is formed in the form of a separating base, ie in the form of a substantially one-piece, flat plate or the like flat part.
• the invention is based on the consideration that a definition of the interface should be equally safe in mechanical and hydraulic terms as well as simple in terms of manufacturing effort.
• the invention has recognized that the determination of the separation surface in the groove in the two-stage heat exchanger can be done in a simple manner and on the other hand allows a secure separation between the high-temperature part and low-temperature part.
• the concept of the invention preferably makes it possible for the first chamber and the second chamber to be separated from one another in a fluid-tight manner by the separating surface.
• the high-temperature part and the low-temperature part depending on requirements and completely fluid-tight against each other sealed.
• a leakage current which is nevertheless comparatively low and needs-based.
• This variability can be achieved by various other types of fixing of the dividing floor in the groove.
• the separating surface for fluid-tight separation of the high-temperature part and low-temperature part for example, be positively connected in the groove.
• the separation surface can also be used under admission of an acceptable leakage rate without further form-fitting measures only in the groove and be held independently by the structural design of the same.
• the concept of the invention allows a needs-adapted type of further sealing measures for further control of a possible leakage rate or to completely suppress the same.
• the heat exchanger is formed in the form of an exhaust gas cooler.
• the first fluid is expediently a recirculated exhaust gas.
• the second and third fluid is in each case in the form of a coolant - when operating at different temperatures - formed.
• the housing from a metal or a non-metal.
• austenitic steel or aluminum has proved to be advantageous as the metal.
• a non-metal in particular a plastic, a fiber composite, a ceramic or mixtures thereof has been found to be useful.
• a separating surface in particular a separating bottom, may consist of a metal or a non-metal.
• stainless steel or aluminum or alloys thereof has proven to be a preferred type of metal.
• a non-metal in particular a plastic or a hard rubber has proven to be particularly advantageous.
• a fiber composite, a ceramic or mixtures thereof is also suitable.
• first chamber and the second chamber can be fluid-tight, in particular leak-free, separated from one another by the separating surface. This is particularly advantageous in the event that the first fluid and the second fluid are different in material, for example, in the case where the first fluid is oil-based and the second fluid is water-based.
• the concept of the invention allows various other possibilities of sealing down the separating surface, in particular of the separating bottom, in the groove.
• the interface is defined with a seal in the groove.
• the parting surface may be defined in the groove via an adhesive.
• it has proved to be advantageous to use the separating surface in FIG To provide a groove associated with the edge region with a rubber and / or a polymer coating. This measure may be provided in addition to or in combination with the aforementioned measures.
• the concept of the invention leads to a first variant of a design which is also referred to as a U-flow arrangement.
• the first chamber and the second chamber are arranged side by side in the housing and the chambers each have juxtaposed flow channels, wherein the flow channels of the first and the second chamber sequentially and in parallel opposite to flow through the first fluid.
• the realization of the separation surface in the form of a separating bottom has proved to be particularly advantageous.
• the housing can be realized in one piece in this first variant, which reduces the component requirement and thus is conducive to a comparatively simple Kassettechniksrea and low cost in the realization of the heat exchanger.
• the flow channels of the first and the second chamber may be of different numbers.
• the heat exchanger can, if necessary, be adapted advantageously to the flow requirements of the first fluid.
• an aforementioned floor can be determined particularly advantageous on the housing according to further developments.
• the bottom is held in an undercut of the housing.
• a bottom may preferably be held in a socket fixed to the housing.
• the seal is arranged in a groove and / or an angle of the housing and / or the floor.
• a heat exchanger has at one end a deflection cap for transferring the first fluid from the flow channels of the first chamber into the flow channels of the second chamber.
• the deflection cap is realized in the form of an uncooled deflection cap. It has been found that, with a suitable design of the first chamber, a deflection of the flow between outflow in the first chamber and backflow in the second chamber can be dispensed with.
• the chamber design can rely mainly on appropriate materials or heat transfer means.
• the bottom in the housing is fixed in such a way that it is sufficiently surrounded by the coolant, that is to say the second and / or third fluid.
• a second variant of the invention provides for the formation of the heat exchanger in a so-called I-flow arrangement.
• the first chamber and the second chamber are arranged on the cross section side one behind the other in the housing and each have one behind the other.
• the flow channels of the first and the second chamber are identical and executed throughout. This measure has proven to be advantageous in terms of cost savings and pressure loss reduction, since this can eliminate a transition point for the first fluid and the number of tubes required for the flow channels is practically halved.
• the housing is made in two parts of two or optionally a plurality of housing parts.
• the groove for fixing the dividing floor can be provided completely in one of the housing parts. It has proven to be particularly preferable for the groove to be formed by both or two adjoining housing parts.
• each of the housing parts can have a nutteilsometimesende formation, which are arranged opposite each other when forming the housing parts to form the groove.
• the housing parts are formed as equal parts. This reduces the number of components to be manufactured in different ways.
• the separating surface is formed in the form of a separating surface which carries the flow channels.
• a separate support of the flow channels formed, for example, by pipes is desired.
• Such support measures can be realized usually via winglet tubes or nubs.
• the separating surface may be formed in the form of a separating bottom. The separating bottom which carries the flow passages can be slid onto the flow passages for attachment and performs the function of separating and supporting parallel adjacent flow passages.
• the separating surface may be formed from a number of separate separating elements.
• the separating surface is composed in a mosaic-like manner by the separating elements. This can be two or more separating elements.
• the number of separating elements corresponds to the number of flow channels.
• a separating element is formed in the form of an annular bead surrounding a flow channel.
• a tube may preferably be thickened in the center of the tube or elsewhere, for example by extrusion coating or otherwise enclosed by means of a separating element.
• a separating element can preferably be made of silicone, plastic or another suitable material, in order to meet the function of the separating surface as a mosaic particle of the separating surface, which is suitable, for example, for sealing.
• each of the separating elements is provided with an adhesive or adhesive in order to ensure that the separating elements adhere to one another, preferably sealingly.
• the separating surface is then advantageously formed in a fluid-tight and stable manner.
• the invention also relates to an exhaust gas recirculation system for an internal combustion engine, comprising an exhaust gas recirculation, a compressor and a heat exchanger according to the concept of the invention in the form of an exhaust gas heat exchanger, in particular in the form of an exhaust gas cooler.
• the invention also leads to an internal combustion engine with an exhaust gas recirculation system of the aforementioned type.
• the invention also leads to the use of the heat exchanger according to the concept of the invention as an exhaust gas cooler for direct or indirect Cooling of exhaust gas in an exhaust gas recirculation system for an internal combustion engine of a motor vehicle.
• the use has proven to be particularly advantageous in passenger cars.
• the concept of the invention has proved to be particularly reliable and advantageous for a heat exchanger in which the first fluid is formed in the form of an exhaust gas and the second and third fluid are formed in the form of a preferably water-based coolant of different temperature.
• a heat exchanger according to the concept of the invention may also be provided in the form of an oil cooler, for example for cooling engine oil and / or gear oil.
• Another possibility is the use as a refrigerant radiator or refrigerant condenser in a refrigerant circuit of an air conditioner.
• the first fluid may also be formed in the form of an oil-based agent or in the form of a refrigerant.
• the second and third fluid may also be of different materials.
• the second fluid could be in the form of an oil-based coolant and the third fluid could be in the form of a water-based coolant.
• Other types of coolant not mentioned here are also possible for use as second and / or third fluid.
• Fig. 1 a particularly preferred embodiment of a heat exchanger in the form of a two-stage exhaust gas cooler according to the first variant of the invention - in view A as a longitudinal section and in view B as a cross section along B-B;
• Fig. 2 different possibilities of a modification A, B, C, D of the detail A in Figure 1A for fixing the bottom of the housing.
• FIG. 3 shows a further modification of the detail A in FIG. 1A in combination with a clipped deflecting cap
• Fig. 4 a particularly preferred embodiment of a heat exchanger in the form of a two-stage exhaust gas cooler according to the second variant of the invention - in view A as a longitudinal section and in view B as a cross section along AA, in view C, the detail C in Fig. 4A is shown;
• FIG. 5 shows an advantageous embodiment of a flow channel in the form of a tube with a separating element for forming a separating surface in the embodiment of FIG. 4.
• FIG. 1 shows a heat exchanger 10 in the form of a two-stage exhaust gas cooler for two-stage heat exchange between a first fluid 1 in the form of an exhaust gas on the one hand and a second fluid 2 in the form of a water-based coolant and a third fluid 3 in the form of a water-based coolant second fluid 2 and the third fluid 3 have different temperatures during operation.
• the second fluid 2 has operating temperatures in the range of about 90 ° to 110 0 C, while the third fluid 3 in operation temperatures in the range of about 40 ° to 60 ° C.
• the heat exchanger 10 has a block 5 for the separate and heat exchanging guidance of the exhaust gas and the coolant.
• the block 5 has a number of flow channels 7A, 7B through which the exhaust gas can flow, which in the present case are formed as winglet tubes and are shown in greater detail in FIG. 1B in cross section.
• the block 5 has a first chamber 9A of the high-temperature part 11 of the exhaust gas cooler receiving the flow channels 7A and permeable by the second fluid 2.
• the block 5 has a second chamber 9B of a low-temperature part 13 which can flow through the third fluid 3 and receives the flow channels 7B.
• the first chamber 9A and the second chamber 9B and the flow channels 7A, 7B are in one aluminum case as one piece for both Chambers 9 A, 9 B jointly formed housing 15 is arranged.
• the first chamber 9A and the second chamber 9B are separated from one another by a separating bottom 17 in the form of a separating plate, with the separating bottom 17 being in a groove (not shown) in the housing 15 and in each case at a both chambers 9A, 9B common limiting bottom 19 abgasein- and downstream or ground 21 is determined abgasumlenk perfume.
• the dividing floor 17 is presently also formed of aluminum.
• the separating plate can also be made of stainless steel.
• the separating plate in both cases, in a soldering of the block 5, the separating plate can also be soldered directly to the deflection-side bottom 21.
• Other modifications can also realize housing 15 made of cast aluminum or stainless steel sheet.
• Non-metal versions of a housing may be formed of plastic. This has the advantage that holder or coolant nozzles - like the present nozzles 14A 1 14B, 16A, 16B - can be injection molded or molded directly onto the housing.
• the deflection-side bottom 21 is presently provided with a deflecting cap 23 and - as explained in more detail with reference to FIGS. 2A to 2D - sealed with a seal 25 against the housing.
• the deflecting-side bottom 21 flows sufficiently around the coolant, so that the deflecting cap 23 can be formed uncooled in this embodiment, which represents a considerable cost saving.
• the housing 15 has an inlet connection 14A for the second fluid 2 in the form of the high-temperature coolant shown here above and a corresponding outlet connection 14B. Furthermore, the housing 15 has an inlet connection 16A shown here below for the third fluid 3 in the form of a low-temperature coolant and a corresponding outlet connection 16B.
• the second fluid 2 is presently provided for cooling the high-temperature part 11 of the heat exchanger 10, while the third fluid 3 is provided for cooling the low-temperature part 13 of the heat exchanger 10.
• the exhaust gas 1 first flows through the high-temperature part 11, is deflected in the deflection cap 23 and fed to the low-temperature part 13.
• the corresponding chamber 9A of the high-temperature part 11 is flowed through by the second fluid 2 in the form of a coolant maintained at a high temperature, between approximately 90 ° and 110 ° C.
• the corresponding chamber 9B of the low-temperature part 13 is replaced by the third fluid 3 in the form of Coolant at low temperature, between about 40 ° to 60 0 C, flows through.
• the entire block 5 including the deflection cap 23 is first encapsulated and then joined either by means of soldering or welding. Subsequently, the block 5 is pushed together with the separating plate in the housing 15.
• the sealing of the chambers 9A, 9B - and thus the sealing of the high-temperature part 11 against the low-temperature part 13 - with respect to the surroundings in the region of the deflection cap 23 takes place by means of the seal 25 in detail A.
• the detail A is with reference to FIGS Fig. 2D shown in more detail.
• the seal is placed in all modifications of FIGS. 2A to 2D such that it is subject to the lowest possible heat input and / or the best possible heat dissipation.
• the separating plate is gummed in the side region, not shown, to the housing.
• the separating plate can also be completely rubber-coated.
• the sealing of the separating plate to the housing may additionally or alternatively be performed by means of an inserted O-ring seal or glued into the housing 15.
• a deflecting cap in a manner shown in detail in Fig. 3 in contrast to Fig. 1 also not be soldered directly to the block 5, but screwed or clipped in a subsequent operation with the housing 15.
• Such a deflection cap is shown in greater detail in FIG. 3 under the reference numeral 27 and clipped over a bottom 21, which in turn is fixed by means of a seal 25 on the housing 15.
• the seal 25 is presently arranged in a groove 29 formed in the wall 29 of the housing 15.
• the bottom 21 is joined to the front side of the wall 29.
• FIGS. 2A to 2D Further possibilities for the connection of a bottom 21 on the housing 15 illustrated with the same reference numbers for the sake of simplicity are shown in FIGS. 2A to 2D.
• FIGS. 2A and 2B show a modification according to which the bottom 21 is held in an undercut 33 of the housing 15. A sealing of the bottom 21 against the housing 15 via a seal 25 in a groove 35 which is formed as shown in FIG. 2A in a wall 29 of the housing 15 and according to FIG. 2B in a wall 37 of the bottom 21st
• FIG. 2C and Fig. 2D A further modification is shown in Fig. 2C and Fig. 2D, according to which the bottom 21 is held in a fixed to the housing 15 bush 39.
• the seal 25 is held in a channel formed by the sleeve 39 and an angle 41 in the wall 29 of the housing 15. This has the advantage that a seal 25 can also be subsequently inserted into the angle 41 of the wall 29 and the bush 39 can be subsequently slipped open.
• the first chamber 9A and the second chamber 9B are arranged side by side in the housing 15 and each have juxtaposed flow channels 7A, 7B, wherein the flow channels 7A, 7B of the first chamber 9A and the second Chamber 9 B are sequentially and parallel flowed through in opposite directions from the first fluid 1 when the heat exchanger 10 is in operation. This can be seen in the corresponding flow directions at reference numeral 1 of FIG.
• FIG 4 shows a further embodiment of a heat exchanger 20 in the form of a two-stage exhaust gas cooler according to the second variant of the invention - in the present case in the so-called I-flow arrangement.
• the first chamber 49A and the second chamber 49B cross-sectional side one behind the other - that is, in the flow direction of the exhaust gas 1 - arranged in the housing 45 and each have one behind the other arranged flow channels 47, wherein the flow channels 47 of the first chamber 49 A and the second chamber 49 B are sequentially and parallel flowed through in the same direction from the first fluid 1 when the heat exchanger 20 is in operation.
• the flow channels 47 of the first chamber 49A and the second chamber 49B are identical, namely formed from a winglet tube 47 common to both chambers 49A, 49B.
• the exhaust gas cooler 20 also has a block 55 for the separate and heat exchanging guidance of the first fluid 1 in the form of an exhaust gas and the second fluid 2 in the form of a first coolant and a third fluid 3 in the form of a second coolant on.
• the flow channels 47 are traversed by the exhaust gas.
• the first chamber 49A is part of a high-temperature part 51.
• the second chamber 49B is part of a low-temperature part 53.
• the first chamber 49A is closed on the flow inlet side by a bottom 61, which is fixed to the housing 45 by holding the flow channels 47.
• the second chamber 49 B is accordingly flow output side limited by a further bottom 63, which is also the flow channels 47 performing holding the housing 45 fixed.
• the housing 45 has an inlet connection 54A and outlet connection 54B for the second fluid 2, this time arranged on different sides, and an inlet connection 56A and outflow connection 56B for the third fluid 3.
• the first chamber 49A and the second chamber 49B are again separated from one another by a separating bottom 57, which is fixed in a groove 65.
• the separating bottom 57 is presently formed in the form of a flow channels 47 in openings 71 performing holding partition, which - like the detail shown in detail C in Fig.
• the housing 45 is formed in two parts with a first housing part 45A for the high-temperature part and a second housing part 45B for the low-temperature part 53. It has proved to be advantageous that both housing parts, as shown in Fig. 4, are formed as the same parts, so that the production cost is substantially reduced.
• the groove 65 is presently formed by opposing protrusions on the first housing part 45A and second housing part 45B after assembly of the housing parts 45A, 45B in the impact plane 69.
• the two housing parts 45A, 45B are designed such that they can receive the separating bottom 57 and prevent it from slipping even in the non-positively joined state.
• the groove 65 which in the present case is formed by both housing parts 45A, 45B formed as identical parts during the assembly thereof.
• a groove may also be formed completely independently in a wall of one of the housing parts 45A, 45B.
• the flow channels 47 in the form of tubes are first encapsulated with the flow-input-side bottom 61, and then the first housing part 45A is pushed over, the separating bottom 57 pushed over and then the second housing part 49B pushed over. Finally, the flow channels 47 designed as tubes are encapsulated with the flow-output-side bottom 63.
• the exhaust gas cooler 20 can now either be completely soldered or welded.
• both housing parts 45A, 45B are advantageously made of aluminum. The tubesheet connections are then welded in the casseted state.
• the tube bottom connections are welded in the coffered state, since the welding process only a small heat input into the Plastic has the housing parts 45A, 45B and thus allows the use of the plastic housing 45A 1 45B.
• the separating bottom 57 is made of hard rubber, or in a modification of plastic. This has the advantage that the separating bottom 57 can be produced with a very small oversize or oversize and can be pushed as a press fit over the flow channels 47 formed as tubes. Due to the properties of the rubber, a sufficiently high tightness between the high-temperature part 51 and the low-temperature 53 results even in the non-positive-locking state. This results in a very significant time and cost savings in the production of the exhaust gas cooler 20.
• the separating bottom 57 may also be formed as a sheet metal part or made of aluminum, which is additionally coated or coated with a polymer or with a rubber for better sealing.
• This has the advantage that the sheet metal or aluminum part fundamentally imparts improved strength to the exhaust gas cooler 20, while the gumming effects a sufficient and, as required, good sealing of the high-temperature part 51 against the low-temperature part 53. Even with this modification, it is possible to push the separating bottom 57 for better sealing as a press fit or at least with the smallest possible gap over the flow channels 47 designed as tubes.
• the separating bottom 57 can be provided, above all, with an adhesive or a sealing compound which seals the gap between the separating bottom 57 and the flow channels 47.
• a curing of an adhesive or sealing dimensions can be done by means of controlled heat.
• Fig. 5 schematically shows an advantageous modification of a flow channel 47 'on which a separator 77 for mosaic formation of a separation surface is held - the latter alternative embodiment of a separation surface may be used to advantage instead of the separation tray 57 in the embodiment of a heat exchanger of Fig. 4A serve.
• the separating element 77 is shown as one on the flow channel 47 '. clip-on silicone or plastic part, if necessary also metal part, formed.
• the partition member 77 may also be glued or soldered to the flow channel 47 'attached or be attached in other ways cloth, form, or friction-fit.
• the adjacent separating elements 77 are brought into contact with one another by arranging adjacent flow channels 47'.
• a system may optionally be carried out with slight pressure on the separating elements - the, preferably yielding, material of the separating elements 77, for example silicone or plastic, then leads to the cascading of the flow channels 47 'to form a fluid-tight interface, which performs the function of in Fig. 4A illustrated dividing floor exerts.
• the separating element can be provided on at least one of its outer part facing an adjacent separating element with an adhesive or adhesive.
• the separating surface can be formed by cohesively juxtaposed separating elements when the flow channels 47 'are cassetted.
• These or similar embodiments have the advantage that a flow channel 47 'together with a partition member 77 can be prefabricated individually and when Kassettieren or installation of the flow channels 47' in the heat exchanger, the separation surface is formed automatically - a separate manufacturing step for the separation surface eliminates practically.
• the flow channels 47 designed as tubes can be made in a great variety of ways, for example with inner rib-side winglets or the like for improving a heat transfer.
• An exhaust gas cooler 10, 20 may be provided in a manner not shown here with a bypass, for example in the form of a tube.
• a bypass can additionally be integrated into the block 55.
• a separation between the high-temperature part 51 and the low-temperature part achieved by the separating bottom 57 can also be achieved in the case of a bypass.
• a further simplification has resulted from the fact that an exhaust gas cooler 10, 20 is completely soldered complete with separating bottom 57, 17.
• the invention is based on a heat exchanger 10, 20, in particular an exhaust gas heat exchanger, for two-stage heat exchange between a first fluid 1 on the one hand and a second 2 and third fluid 3 different temperature on the other hand, comprising: a block 5, 55 for separate and heat exchanging leadership of the first 1 and of the second 2 and third fluid 3, with a number of flow channels 7A, 7B 1 47 through which the first fluid 1 can flow, a first chamber 9A, 9B receiving the flow channels 7A, 7B, 47, through which the second fluid 2 can flow High temperature part 11, 51 and a second the flow channels 7A, 7B, 47, through which the third fluid 3 can flow through chamber 9A, 9B of a low-temperature part 13, 53, and a housing 15, 45, 45A, 45B, in which the first 9A, 49A and second chambers 9B, 49B and the flow channels 7A, 7B, 47 are arranged.
• the concept of the invention enables a cost-effective realization of such a two-stage heat exchanger with a lower leakage between the high-temperature part 11, 51 and the low-temperature part 13, 53.
• the concept envisages that the first chamber 9A, 49A and the second chamber 9B, 49B by a separating surface 17, 57, preferably fluid-tight, are separated from each other, which is fixed in a groove 65.

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• Engineering & Computer Science (AREA)
• Physics & Mathematics (AREA)
• Thermal Sciences (AREA)
• Mechanical Engineering (AREA)
• General Engineering & Computer Science (AREA)
• Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
• Exhaust-Gas Circulating Devices (AREA)

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• 2008
  • 2008-01-31 WO PCT/EP2008/000750 patent/WO2008092677A1/de active Application Filing
  • 2008-01-31 DE DE102008007073A patent/DE102008007073A1/de not_active Withdrawn
  • 2008-01-31 EP EP08707439A patent/EP2115375A1/de not_active Withdrawn
• 2009
  • 2009-07-31 US US12/533,468 patent/US8627882B2/en not_active Expired - Fee Related

Non-Patent Citations (1)

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