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
  • F28D7/10—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 one within the other, e.g. concentrically
  • F28D7/106—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 one within the other, e.g. concentrically consisting of two coaxial conduits or modules of two coaxial conduits
• • 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
  • F28D9/00—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
  • F28D9/0031—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other
  • F28D9/0043—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another
  • F28D9/0056—Heat-exchange apparatus having stationary plate-like or laminated conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for one heat-exchange medium being formed by paired plates touching each other the plates having openings therein for circulation of at least one heat-exchange medium from one conduit to another with U-flow or serpentine-flow inside conduits; with centrally arranged openings on the plates
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F1/00—Tubular elements; Assemblies of tubular elements
  • F28F1/02—Tubular elements of cross-section which is non-circular
  • F28F1/022—Tubular elements of cross-section which is non-circular with multiple channels
• • 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
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F2250/00—Arrangements for modifying the flow of the heat exchange media, e.g. flow guiding means; Particular flow patterns
  • F28F2250/06—Derivation channels, e.g. bypass
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F28—HEAT EXCHANGE IN GENERAL
  • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
  • F28F2255/00—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes
  • F28F2255/14—Heat exchanger elements made of materials having special features or resulting from particular manufacturing processes molded

Definitions

• the invention relates to a heat transfer unit with a channel through which a coolant flows and a channel through which a fluid to be cooled flow, which are separated from one another by a wall, from which ribs extend in at least one of the two channels.
• Such heat transfer units are used for example for exhaust gas cooling in an exhaust gas recirculation train in an internal combustion engine.
• the ribs usually protrude into the channel through which the fluid to be cooled flows.
• the ribs extend from the two opposite sides of the heat transfer unit into the channel, as well as cooling devices in which the ribs only extend from one side into the channel.
• the ribs may take on different shapes and either extend integrally along the main flow direction or be formed as a single ribs, here both pin and tubular as well as wing-shaped ribs are known.
• the channel through which the coolant flows can be arranged both within the channel through which the fluid to be cooled and also surrounding it in cross-section.
• heat transfer units are used for example for air, exhaust or oil cooling.
• intercoolers serve to reduce the combustion temperatures and thus the resulting nitrogen oxides and exhaust gas cooler for heating the air for faster heating of a passenger compartment or in the exhaust system to reduce the exhaust gas temperature of a gas flowing to a catalyst.
• exhaust gas recirculation lines are using the exhaust gas cooler set the exhaust gas temperatures and thus the combustion temperature in the engine, which in turn pollutant emissions can be reduced.
• the cooling water of the internal combustion engine serve as a coolant, the cooling water of the internal combustion engine.
• a heat transfer unit which is arranged in an exhaust gas recirculation system of an internal combustion engine is known, for example, from DE 10 2004 019 554 A1.
• This consists of an inner U-shaped flowed through by exhaust gas channel, which is surrounded over the entire cross-section of a coolant-flow channel.
• This is a multi-part die-cast cooler, which has different graduation levels.
• the known heat transfer units have only low cooling capacities and cooler efficiencies, in particular at low throughputs and temperature differences. However, especially in the field of exhaust gas recirculation, it may be desirable to further reduce the pollutant emissions to achieve a high cooling capacity at low pressure loss, both at high and at low flow rates.
• the channel through which the fluid to be cooled has a fluid inlet and a fluid outlet, wherein the channel through a downstream extending partition into a first and a second sub-channel having a first fluid part inlet and a second fluid part inlet and a first fluid part outlet and a second fluid part outlet is separated, wherein at least the first fluid part inlet is closed by a shut-off device.
• the heat transfer unit has a wall which separates the fluid inlet from the fluid outlet and extends up to an end of the heat transfer unit opposite the fluid inlet or outlet, so that the heat transfer unit flows through in a U-shaped manner at least when the first shut-off device is open.
• a wall which separates the fluid inlet from the fluid outlet and extends up to an end of the heat transfer unit opposite the fluid inlet or outlet, so that the heat transfer unit flows through in a U-shaped manner at least when the first shut-off device is open.
• shut-off devices are arranged in the heat transfer unit, wherein when the first fluid part inlet is closed by means of the first shut-off device, the second shut-off device is connected in such a way that the cooling path for the fluid in the heat transfer unit lengthens.
• the shut-off devices are arranged such that the heat transfer unit is flowed through in part by the second barrier in the opposite direction.
• the heat transfer unit has two partitions, which cooperate with the shut-off devices in such a way that the entire channel flows through in both switching positions of the shut-off devices, wherein the cooling section extends when the cross-section narrows. It
• the entire available cross-section of the heat transfer unit is used in both switching positions of the shut-off device, which in turn leads to an increase in efficiency.
• the cooling section preferably extends substantially to the same extent as the cross section through which it flows decreases. This means that when halving the flow-through cross section, the cooling section is doubled. This can be achieved by using the entire heat transfer unit in both switching positions of the shut-off devices and by multiple deflection.
• the use of the entire available heat transfer surface in both switching positions of the shut-off to increase the efficiency is achieved in particular by a heat transfer unit, in which the first partition from the fluid inlet between the first and the second fluid part inlet in the main flow direction in the heat transfer unit until before the Fluid inlet the opposite end extends and the second partition from the fluid outlet between the first and the second Fluidteilauslass in the main flow direction in the heat transfer unit extends to the opposite end to the fluid outlet, the first and second Absperreinrich- device are designed as a flap and the flaps on the opposite ends of the heat transfer unit are each arranged between the first and the second partition, wherein the flaps are arranged perpendicular to each other in both switching positions.
• the first partition wall extends in a U-shape from the fluid inlet between the first and second fluid part inlets in the main flow direction to before
• the second fluid-part outlet and the second partition wall extend in a U-shape from the fluid outlet between the first and the second fluid part outlet in the main flow direction up to the first fluid part inlet, wherein the first and the second shut-off device are designed as a flap, wherein the first flap is the first fluid - idileinlass is closed and can be closed by the second flap of the second Fluidteilauslass, the flaps open and close parallel to each other.
• the flow-through cross-section is divided by three with the first fluid part inlet closed and at the same time the cooling section tripled so that a very good cooling effect is achieved with even lower throughputs or fluid mass flows due to the long existing cooling section and the small cross section.
• the pressure loss across the cooler can be kept low.
• Figure 1 shows a plan view of a first embodiment of a heat transfer unit according to the invention in a sectional view.
• FIG. 2 shows a section through the heat transfer unit according to FIG. 1 along the line A-A
• FIG. 3 shows a plan view of an alternative heat transfer unit according to the invention.
• FIG. 4 shows a further alternative embodiment of a heat transfer unit according to the invention, again in a top view and a sectional representation.
• FIGS. 1 and 2 show a first embodiment of a heat transfer unit 1 according to the invention, which is preferably used as an exhaust gas heat exchanger in motor vehicles. It consists of an outer housing 2, in which an inner housing 3, which can be produced, for example, by die-casting, is arranged. Inside the inner housing 3, a coolant-flow channel 5 is arranged, the inlet and outlet nozzles 6, 7 are shown in Figure 2 and which in. Between the inner housing 3 and the outer housing 2 is formed by a flowing through the fluid to be cooled channel 4 present embodiment are arranged at one of a fluid inlet 8 and a fluid outlet 9 opposite end 10 of the heat transfer unit.
• a fluid inlet 8 and a fluid outlet 9 opposite end 10 of the heat transfer unit.
• the coolant-flow channel 5 is delimited by a wall 11 which runs around in cross-section and from which ribs 12 extend into the channel 4 through which the fluid to be cooled flows.
• the channel 4 through which the fluid to be cooled flows is designed such that its fluid inlet 8 is arranged on the same side of the head as the fluid outlet 9, so that the fluid to be cooled is deflected by 180 ° at the opposite end 10. Accordingly, the ribs 12 are arranged in this region following the main flow direction.
• the ribs 12 viewed in the main flow direction, are arranged next to one another in rows, with a second row each ending with the conclusion of a first row, whose ribs 12 follow the ribs
• the heat transfer unit additionally has a first partition wall 14, which extends in a U-shape from the fluid inlet 8 via the end 10 to the fluid outlet 9.
• this dividing wall 14 divides the channel 4 into two partial channels 15 and 16 and thus also the fluid inlet 8 and the fluid outlet 9 into two approximately equal-sized fluid-part inlets 17, 18 and two fluid-part outlets 19, 20.
• the first fluid-part inlet 17 becomes controlled by a shut-off device 21 in the form of a flap whose axis of rotation 22 is arranged in the present embodiment in extension to the outer housing 2.
• both the shut-off device 21 and the partition wall 14 extend over the entire height of the heat transfer unit 1.
• an exhaust gas recirculation valve is usually formed in front of the heat transfer unit 1, so that different fluid mass flows or exhaust gas mass flows are supplied to the heat transfer unit 1.
• the cooling capacity of a heat transfer unit without partition 14 and shut-off device 21 is only very small.
• the first fluid inlet 17 is closed by the shut-off device 21, so that the entire mass flow flows via the second fluid inlet 18 to the second fluid outlet 20. This is in comparison to a heat transfer unit 1 without disconnectable Channel only half the cross-section available.
• shut-off device 21 is opened, so that the entire cross-section of the channel 4 is available for cooling, so that no excessive pressure losses occur and at the same time the known good cooling effect is achieved.
• FIG. A further embodiment is shown in FIG. Compared to the first embodiment, two partition walls 23 and 24 are arranged in this heat transfer unit 1, of which the first partition wall 23 extends from the fluid inlet 8 to the opposite end 10 of the heat transfer unit 1 and the second partition wall 24 extends from the fluid outlet 9 to the opposite end 10 Heat transfer unit 1 extends. Both partitions 23, 24 terminate at a sufficient distance from the end 10, so that when closing one of the fluid part inlets 17, 18 a sufficient cross-section for the flow of fluid behind the ends of the partition walls 23 and 24 and the outer housing 2 is available.
• axes of rotation 25 Between the respective ends of the two partitions 23, 24 in extension to the wall 13 are axes of rotation 25, 26 are arranged, on each of which a shut-off device in the form of a flap 27, 28 is mounted.
• the width of the flaps 27, 28 corresponds to the distance between the two partitions 23, 24.
• the width of the end of the wall 13 of the axes of rotation 25, 26 each half the width of such a flap 27, 28, so that the first flap 27 in its first position shuts off the first fluid part inlet 17 and the first fluid part outlet 19, while the second flap 28 is arranged offset in its first end position by 90 ° to the first flap 27 and thus in its width with one end against the wall 13th abuts and rests against the outer housing 2 with its other end.
• the first flap 27 In its second position, the first flap 27 abuts with its two ends against the partitions 23 and 24. If now the first shut-off device 27 in a position in which it rests against the two partitions 23, 24, the first fluid part inlet 17 is closed. The fluid mass flow thus enters the partial passage 16 via the second fluid part inlet 18 and from here to the opposite end 10 of the heat transfer unit 1.
• the second shut-off device 28 now prevents a fluid mass flow beyond the extension of the wall 13 due to its above-mentioned first position. Consequently, the fluid mass flow undergoes a 180 ° turn and passes behind the dividing wall 23 into the partial passage 15, but flows through it in the opposite direction, ie in the direction of the first fluid inlet inlet 10.
• FIG. 4 shows a further alternative heat transfer unit 1 in which in turn two partitions 29, 30 and two shut-off devices 31, 32 are used. However, in this case, the first dividing wall 29 runs from the fluid inlet 8 in a U-shaped manner to the fuel inlet.
• the fluid inlet 8 and the fluid outlet 9 are divided in approximately their cross-section or in their width.
• shut-off devices 31, 32 are arranged on axes of rotation 33, 34 which are arranged in extension to the ends of the dividing walls 29, 30 in the region of the fluid part inlets 17, 15 and 18, respectively, or fluid part outlets 19, 20.
• the illustrated embodiments of the heat transfer unit allow use with very good cooling performance and cooler efficiencies over a wide range of throughput and temperature. At the same time, the pressure loss across the cooler is kept as small as possible.

Landscapes

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

Applications Claiming Priority (2)

Publications (2)

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ID=37944189

Family Applications (1)

Country Status (7)

Families Citing this family (13)

Family Cites Families (22)

• 2006
  • 2006-03-16 DE DE102006012219.4A patent/DE102006012219B4/de not_active Expired - Fee Related
• 2007
  • 2007-01-25 EP EP07712105A patent/EP1994349B1/fr not_active Not-in-force
  • 2007-01-25 WO PCT/EP2007/050720 patent/WO2007104595A1/fr not_active Ceased
  • 2007-01-25 AT AT07712105T patent/ATE530868T1/de active
  • 2007-01-25 ES ES07712105T patent/ES2373064T3/es active Active
  • 2007-01-25 JP JP2008558739A patent/JP5039065B2/ja not_active Expired - Fee Related
  • 2007-01-25 US US12/293,156 patent/US8403031B2/en not_active Expired - Fee Related

Non-Patent Citations (1)

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