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
  • F28D7/16—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
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
  • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
  • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
  • F02M26/23—Layout, e.g. schematics
  • F02M26/25—Layout, e.g. schematics with coolers having bypasses
  • F02M26/26—Layout, e.g. schematics with coolers having bypasses characterised by details of the bypass valve
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
  • F02M26/00—Engine-pertinent apparatus for adding exhaust gases to combustion-air, main fuel or fuel-air mixture, e.g. by exhaust gas recirculation [EGR] systems
  • F02M26/13—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories
  • F02M26/22—Arrangement or layout of EGR passages, e.g. in relation to specific engine parts or for incorporation of accessories with coolers in the recirculation passage
  • F02M26/29—Constructional details of the coolers, e.g. pipes, plates, ribs, insulation or materials
  • F02M26/32—Liquid-cooled heat exchangers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F27/00—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus
  • F28F27/02—Control arrangements or safety devices specially adapted for heat-exchange or heat-transfer apparatus for controlling the distribution of heat-exchange media between different channels
• • 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

Definitions

• the invention relates to a heat exchanger for combustion engines according to the preamble of claims 1, 7, 21 and 24.
• DE 102 03 003 A1 describes a heat exchanger for exhaust gases, in which a first and a second flow channel for exhaust gases are arranged in parallel in a common housing, wherein a flow channel upstream valve channel has the same flow direction as the flow channels, that is arranged linearly to the flow channels ,
• valve element is not in the same flow axis as the flow channels, as thus formed by the pulsating exhaust gas flow of internal combustion engines, speed-dependent standing waves affect less on the mechanics of the valve element.
• longitudinal and transverse vibrations of the heat exchanger housing are reduced in the region of the valve channel, which is also favorable for the function and life of the valve mechanism.
• the valve channel in the flow direction of the exhaust gases, is arranged in front of the flow channels and an inlet channel in front of the valve channel, wherein particularly preferably a flow axis of the inlet channel has a different direction than the flow axis of the valve channel and as the flow axis of the flow channels.
• a stepwise curvature of the exhaust system is made possible, so that an unhindered exhaust gas flow is ensured with a total of small construction.
• An angle between the flow axis of the valve channel is particularly preferred and the flow axis of the inlet channel is greater than 30 degrees in order to achieve a sufficiently large deflection of the exhaust gas stream.
• an angle between the flow axis of the valve channel and the flow axis of the flow channel is greater than 30 degrees, more preferably greater than 40 degrees.
• the angle between the flow channel and valve channel and valve channel and inlet channel can add in terms of the exhaust system to achieve a total of particularly a large deflection of the exhaust stream, without taking into account disadvantages associated with significant extent in purchasing.
• an unfavorable in terms of turbulence and flow resistance exhaust system which forces a deflection of the exhaust gas flow of 90 degrees in the smallest space is effectively avoided.
• an angle between the flow axis of the valve channel and the flow axis of the flow channel is particularly preferably less than 60 degrees. This does not preclude the aforementioned two-stage diversion of the exhaust flow to total angles of up to about 90 degrees.
• an average flow length of one of the flow channels is at least a factor of two, more preferably a factor of 2.5, greater than an average flow length of the valve channel.
• flow length is understood to be the mean path length of the exhaust gases, that is to say the path along an axis of symmetry of an exhaust gas duct.
• the valve element has exactly one adjustable flap element, so that only a small number of components is required.
• the flap element is preferably accommodated on a rotatable shaft which can be driven.
• valve channel has a dividing wall adjoining the flap element, the valve channel being divided by the dividing wall at least in sections into two valve channel halves. This allows both a simple design and a low-swirl exhaust system.
• the second flow channel is arranged substantially parallel to the first flow channel, and particularly preferably the first flow channel and the second flow channel are accommodated in a common housing. As a result, a compact construction of the heat exchanger is favored in each case.
• the valve channel in this case has a circular cross section, and the shaping can be formed by deformation of a wall of the valve channel, in particular by embossing.
• the molding is simple and inexpensive to produce.
• the object of the invention is further achieved by the characterizing features of claim 18. Due to the double wall of the second flow channel, a particularly good insulation of the exhaust gas flowing through this channel is made possible against a heat exchange.
• the second flow channel in this case comprises an inner tube, which is accommodated in a housing, wherein an outer surface of the inner tube is spaced from the housing.
• the spacing of the housing to the inner tube can be advantageously fixed by means of distance means.
• These may comprise a plurality of nubs arranged on the outer surface of the inner tube, whereby a double wall of the second flow channel with good thermal insulation can be realized by simple means.
• the inner tube is connected directly to a guide plate, wherein the guide plate is arranged in the valve channel.
• the valve element is particularly advantageously arranged movably on the guide plate, and the valve channel is connected directly to the housing.
• the object of the invention is also achieved with the characterizing features of claim 27. Due to the at least two-part design of the valve channel housing, it is advantageously possible to produce a complex shape of the valve channel in terms of an optimized exhaust system in a simple manner.
• valve element is received between the first and the second housing part, wherein it is particularly advantageous movably mounted on at least one of the housing halves.
• the housing parts are firmly connected to each other, in particular by means of welding.
• a high gas-tightness can be combined with a high temperature resistance.
• other temperature resistant connections such as brazing may be provided.
• a connection of the housing parts by means of screwing or riveting or crimping is possible, with regard to the gas tightness depending on the requirement, if necessary, additional sealing means are provided.
• At least one of the housing parts is preferably designed as a formed part, in particular a deep-drawn part.
• This also advantageously allows the use of materials whose manufacture is problematic via casting processes, such as stainless steel.
• the two-part design of the valve channel does not contradict any of the aforementioned features of the invention, so that each of the features mentioned can be combined with the two-part design of the valve channel.
• these formations of the valve channel wall can advantageously already be formed by way of the forming process.
• Fig. 1 shows a plan view of a first embodiment of a heat exchanger according to the invention from above.
• Fig. 2 shows the heat exchanger of FIG. 1 rotated by 90 °.
• Fig. 3 shows the heat exchanger of FIG. 2 rotated by 90 °.
• Fig. 4 shows a frontal plan view of the heat exchanger according to
• FIG. 1 shows a schematic sectional drawing through the valve channel of the heat exchanger in the orientation according to FIG. 2.
• FIG. 6 shows a cutaway spatial representation of a
• FIG. 7 shows a three-dimensional representation of a second exemplary embodiment of a heat exchanger according to the invention.
• Fig. 8 shows a detail view of the heat exchanger of Fig. 7, wherein the interior of the valve channel is shown.
• Fig. 9 shows a perspective view of the valve element of the
• FIG. 10 shows a three-dimensional view of a third embodiment of a heat exchanger according to the invention, wherein internal components of the heat exchanger are partially shown.
• FIG. 11 shows a schematic plan view from above of a detail of FIG.
• FIG. 12 shows a schematic plan view of the detail of Fig. 11 from the side.
• Fig. 13 shows a schematic plan view of the detail of Fig. 11 from the front.
• FIG. 14 shows a schematic plan view of an inner tube of the heat exchanger from FIG. 10 to FIG. 8.
• FIG. 15 shows a perspective view of a detail of a heat exchanger according to the invention.
• FIG. 16 shows a perspective view of a modification of a valve channel of the second exemplary embodiment of a heat exchanger according to FIG. 7 to FIG. 9.
• Fig. 17 shows the valve channel of Fig. 16 from another spatial
• FIG. 18 shows the valve channel of Fig. 16 from another spatial
• the heat exchanger according to the invention according to the first embodiment comprises a first flow channel 1 and a second flow channel 2, wherein in the present case, the first flow channel is formed as a majority of parallel individual channels (see Fig. 6).
• Fig. 6 shows that the two flow channels are arranged parallel to each other and housed in the same housing 3.
• a conduit 4 for guiding a liquid coolant is also guided in the housing 3 and emerges from the housing at an inlet-side port 4a and an outlet-side port 4b, respectively.
• the line 4 is within the housing only with the first flow channel in substantial thermal contact, so that a relevant heat exchange between the exhaust gas and the coolant takes place only when the first flow line 1 is flowed through by the exhaust gas.
• the heat exchanger has in the flow direction S of the exhaust gases at the end an outlet channel 5, which is aligned here in terms of the exhaust gas flow parallel to the flow channels.
• the outlet channel 5 extends at an angle to the flow channels 1, 2.
• valve channel 6 In the flow direction S in front of the flow channels 1, 2, a valve channel 6 is arranged, which is welded to the housing 3.
• the valve channel 6 has a circular cross-section and is attached to the housing 3 at an angle W1 of approximately 42 ° with respect to the flow channels 1, 2. This angle exists between an input-side flow axis SV and respective flow axes SK1, SK2 of the first flow channel 1 and second flow channel 2 (see FIG. 2).
• an inlet channel 7 is welded, the input side via a flange 7a with the other
• Exhaust pipe is connectable.
• Inlet duct closes with the input-side flow axis SV of the
• Valve channel an angle W2 of 35 °.
• the angles W1 and W2 lie in a plane so that the flow axes SE of the inlet channel and the flow axes SK1, SK2 of the flow channels 1, 2 enclose an angle of 77 ° in total.
• the angles can also be in lie different levels and deviate from the existing values in order to allow adaptation to a particular given exhaust system.
• valve channel 6 formed as a drivable flap movable flap element 8 is received (see Fig. 5).
• the flap 8 is fixedly connected to a rotatable shaft 9, which extends along an end edge of the flap 8 and vertically through the valve channel 6.
• a fixed baffle 10 is provided in the valve passage, which serves as a continuation of the valve flap, due to the baffle 10 is an outlet-side end portion of the valve channel into a first valve channel half 6a and a second valve channel half 6b divided, each of the valve channel halves 6a, 6b respectively one of the flow channels 1, 2 are connected.
• the flap 8 is bent or elliptically shaped at its edge opposite the shaft 9 in order to achieve a sealing fit to the wall of the valve channel 6 which is circular in cross-section.
• the wall of the valve channel in the area of the system of the valve flap have a corresponding processing.
• the flap 8 is movable via a drive 11 of the shaft 9, wherein the drive 11 in this case comprises a vacuum box 12 through which a push rod 13 is movable.
• the push rod 14 is connected at the end with a shaft 9 fixed to the pivot pin 13 via a ball joint. This results in a push or pull movement of the push rod 14 to a rotation of the shaft 9 and thus to an adjustment of the flap 8.
• exhaust gas can not, at any proportion or completely passed through the heat exchange serving first flow channel 1 become.
• the dimensioning of the heat exchanger is advantageously designed so that it is a total of small construction, without hindering the exhaust gas flow. middle
• Flow lengths of the two flow channels 1, 2 are in each case the same and correspond to the geometric length of the two channels.
• An average flow length of the valve channel 6 is approximately the geometric length of a center line of the valve channel 6.
• the mean flow length of a flow channel 1, 2 is approximately 2.7 times greater than the average flow length of the valve channel 6.
• the heat exchanger according to the second embodiment has, as in the first exemplary embodiment, a valve channel 6 which is arranged at an angle to the flow channels 1, 2.
• the valve element 15 comprises a baffle 10, on which a valve flap 8 accommodated on a shaft 9 is arranged.
• the valve channel 6 comprises a section of substantially circular cross-section. Formations are provided in the wall of this section, against which an edge region 8a of the flap 8 rests flat when the flap is in an end position.
• the system to the first formation 16 is the passage of the exhaust gas flow through the second flow channel 2 and the system to the formation 17 associated with the passage through the first flow channel 1.
• Fig. 8 shows the passage through the second flow channel.
• the formations 16, 17 are each made by pressing a correspondingly shaped punch in the wall of the valve channel 6, so that they are visible from the outside. Due to the flat contact of the flap 8 on the formations 16, 17, the seal of the flap is improved and a vibrating striking the flap against the wall of the valve channel 6 is reduced.
• the valve element 15 has, according to FIG. 9, a first bearing 18 and a second, spaced bearing 19.
• the shaft 9 is connected to each of the
• Breakthrough of the valve channel is assigned and the second bearing 19 a bag-like receptacle on the valve channel 6 on the opposite side of the breakthrough. But it can also be provided that is dispensed to the second bearing 19, so that the shaft is received only in the region of a passage through the valve channel 6 at a single bearing 18 rotatably mounted on the valve channel 6.
• the heat exchanger according to the third exemplary embodiment (FIGS. 10 to 14), in contrast to the previous exemplary embodiments, has a valve channel 6 ', which is aligned parallel to the flow channels 1, 2.
• the heat exchanger comprises a housing 3, in which a total of fifteen parallel tubes 1 a are arranged, which together form the first flow channel 1.
• the walls of the tubes 1a are directly flowed around by the coolant flowing through the housing 3.
• the second flow channel 2 is also accommodated in the housing 3.
• the flow channel 2 comprises an inner wall 3a, which is shown in FIG. 11 and FIG. 13 as a dashed line and is designed as a two-sided open, tubular passage through the housing 3.
• the second flow channel comprises an inner tube 20 which is inserted into the passage.
• An outer surface of the inner tube 20 includes a number of spacer means 21, which are formed as projecting nubs on the outer surface of the inner tube 20.
• the studs 21 touch the inner wall 3a of the housing 3 (see in particular Fig. 13), so that the thermal contact between the from Coolant flow around the housing and the exhaust gas flowed through the inner tube 20 is very small.
• a double wall of the second flow channel 2 with a first wall (housing passage 3a) and a second wall (inner tube 20) is formed by the described arrangement.
• the inner tube 20 and the passage 3a of the housing have an elongated cross section and close at their end faces flush with each other.
• FIG. 15 shows a valve channel with angled orientation, but corresponds with regard to the arrangement and fixing of the housing 3, inner tube 20 and valve element 15 to the third exemplary embodiment.
• the representation of Fig. 15 shows a preferred sequence of mounting and fixing the components:
• the baffle 10 comprises an angled edge 10 a with a cross-section of the inner tube 20 adapted aperture.
• the baffle 10 is welded to an end face of the inner tube 20 around the edge of the opening around.
• This unit is then inserted into the passage 3a of the housing 3, wherein due to the knobs 21 regularly a good frictional retention of the inner tube is achieved.
• the inner tube and / or the guide plate 10 is welded to the housing, where appropriate, a Anticianen is sufficient.
• FIGS. 16 to 18 show a particularly advantageous modification of the inventive heat exchanger according to the second exemplary embodiment.
• the reference to the second exemplary embodiment is only an example and the modification can also be combined with each of the other exemplary embodiments.
• the outer wall of the valve channel is not formed as a one-piece housing, but includes a valve channel housing 30 which is composed of a first housing part 31 and a second housing part 32.
• the present two housing parts are formed substantially as mirror-symmetrical halves, the symmetry plane extending perpendicularly through the shaft 9 of the valve element 9, 10, 11.
• the mirror symmetry is not accurate because the shaft 9 passes through the first housing part 31 and is rotatably mounted on the first housing part 31 in the region of the passage.
• On the second housing part 32 no bearing of the shaft 9 is provided in the example shown.
• the shaft 9 may also be additionally supported in a corresponding recess of the second housing part 32.
• Each of the housing parts has a part of a respective shaping 16, 17 already described in the second exemplary embodiment for the planar contact of the valve flap 8. In the drawings Fig. 16 to Fig. 18, the valve flap 8 is not shown for clarity.
• the guide plate 10 shown in FIGS. 16 to 18 extends substantially perpendicular to the said symmetry or sectional plane of the valve channel housing.
• the baffle 10 end-tip formations 10a, which engage in corresponding edge-side formations of the housing parts 31, 32 and by means of which the baffle 10 between the assembled housing parts 31, 32 is supported.
• additional welding of baffle 10 and housing parts 31, 32 may be provided.
• the baffle 10 is not firmly connected to the shaft 9 but only extends to its immediate vicinity or slidably applied to the shaft with a correspondingly accurate adjustment.
• Each of the housing parts 31, 32 has been made by forming by deep drawing from a corresponding blank.
• the housing parts which are particularly advantageously made of stainless steel, fixed by welding together.
• valve flap 8 is connected to its shaft 9 (usually by welding) and rotatably inserted into the first housing part 31. Subsequently, the housing parts 31, 32 are fixed to each other by means of welding. Depending on whether the baffle 10 is clamped and / or secured by welding, its assembly and fixing before or after welding of the housing parts or even before and in part done after.
• the inner tube 20 of the third exemplary embodiment After the baffle 10 has been fixed, when using the inner tube 20 of the third exemplary embodiment, first the inner tube 20 can be welded to the baffle 10. A correspondingly advantageous embodiment of the guide plate 10 can be taken from the description of the third embodiment.
• valve channel 6 with the housing 3, possibly with insertion of the inner tube 20, brought together and welded to the housing 3 gas-tight.
• the respective special features of the exemplary embodiments described are not limited to these, but can be combined freely with each other, wherein, if appropriate, by means of certain combinations, particularly advantageous heat exchangers can be formed.
• molding, mounting and mounting of the inner tube 20 are applicable to the first two embodiments, and the molds 16, 17 of the valve channel for engaging the valve flap 8 are not limited to angular orientation valve channels.

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

Applications Claiming Priority (2)

Publications (1)

Family

ID=35501252

Family Applications (1)

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• 2004
  • 2004-09-15 DE DE102004045021A patent/DE102004045021B4/de not_active Expired - Fee Related
• 2005
  • 2005-08-29 WO PCT/EP2005/009285 patent/WO2006029700A2/de active Application Filing
  • 2005-08-29 US US11/575,366 patent/US20070295483A1/en not_active Abandoned
  • 2005-08-29 BR BRPI0515298-4A patent/BRPI0515298A/pt not_active IP Right Cessation
  • 2005-08-29 CN CN2005800387615A patent/CN101057071B/zh not_active Expired - Fee Related
  • 2005-08-29 EP EP05794472A patent/EP1794437A2/de not_active Withdrawn
  • 2005-08-29 JP JP2007530621A patent/JP2008513646A/ja active Pending
  • 2005-08-29 MX MX2007003016A patent/MX2007003016A/es active IP Right Grant

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