WO2011107282A1 - Dispositif pour l'utilisation de la chaleur des gaz d'échappement - Google Patents

Dispositif pour l'utilisation de la chaleur des gaz d'échappement Download PDF

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Publication number
WO2011107282A1
WO2011107282A1 PCT/EP2011/001051 EP2011001051W WO2011107282A1 WO 2011107282 A1 WO2011107282 A1 WO 2011107282A1 EP 2011001051 W EP2011001051 W EP 2011001051W WO 2011107282 A1 WO2011107282 A1 WO 2011107282A1
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WO
WIPO (PCT)
Prior art keywords
flow
flow channel
heat
teg module
teg
Prior art date
Application number
PCT/EP2011/001051
Other languages
German (de)
English (en)
Inventor
Christian Vitek
Martin Adldinger
Boris Kienle
Robin Willats
Original Assignee
Faurecia Emissions Control Technologies, Germany Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE202010003049U external-priority patent/DE202010003049U1/de
Priority claimed from DE202010007872U external-priority patent/DE202010007872U1/de
Application filed by Faurecia Emissions Control Technologies, Germany Gmbh filed Critical Faurecia Emissions Control Technologies, Germany Gmbh
Publication of WO2011107282A1 publication Critical patent/WO2011107282A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N5/00—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy
    • F01N5/02—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat
    • F01N5/025—Exhaust or silencing apparatus combined or associated with devices profiting by exhaust energy the devices using heat the device being thermoelectric generators
    • H—ELECTRICITY
    • H10—SEMICONDUCTOR DEVICES; ELECTRIC SOLID-STATE DEVICES NOT OTHERWISE PROVIDED FOR
    • H10N—ELECTRIC SOLID-STATE DEVICES NOT OTHERWISE PROVIDED FOR
    • H10N10/00—Thermoelectric devices comprising a junction of dissimilar materials, i.e. devices exhibiting Seebeck or Peltier effects
    • H10N10/10—Thermoelectric devices comprising a junction of dissimilar materials, i.e. devices exhibiting Seebeck or Peltier effects operating with only the Peltier or Seebeck effects
    • H10N10/13—Thermoelectric devices comprising a junction of dissimilar materials, i.e. devices exhibiting Seebeck or Peltier effects operating with only the Peltier or Seebeck effects characterised by the heat-exchanging means at the junction
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01N—GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR MACHINES OR ENGINES IN GENERAL; GAS-FLOW SILENCERS OR EXHAUST APPARATUS FOR INTERNAL COMBUSTION ENGINES
    • F01N2410/00—By-passing, at least partially, exhaust from inlet to outlet of apparatus, to atmosphere or to other device
    • F01N2410/02—By-passing, at least partially, exhaust from inlet to outlet of apparatus, to atmosphere or to other device in case of high temperature, e.g. overheating of catalytic reactor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to a device for exhaust heat utilization in internal combustion engines of motor vehicles.
  • the exhaust heat is transferred by means of a heat exchanger to the cooling medium of a cooling circuit in order to achieve the fastest possible and uniform heating of the individual engine components via the cooling circuit.
  • the desired operating temperature can be achieved faster and beyond the component wear, the fuel consumption and pollutant emissions to reach the operating temperature significantly reduced.
  • thermoelectric generator modules (hereinafter TEG modules) are already known from the prior art, which convert thermal energy into electrical energy and can be used in exhaust systems.
  • Such a device for exhaust heat utilization by means of TEG modules is described for example in JP 11229867 A.
  • a bypass line is provided in this Japanese document, which upstream of the Device for exhaust heat utilization branches off an exhaust pipe and opens downstream of the device for exhaust heat recovery again in the exhaust pipe.
  • the distribution of the exhaust gas flow between the exhaust pipe and the bypass line is adjusted by an electrically operated flow control valve.
  • This proposed bypass construction is intended to prevent overheating of the TEG modules, but also has a high space and material requirements for pipelines, whereby the assembly is expensive and the overall system is expensive.
  • the object of the invention is to provide a compact and inexpensive device for waste heat recovery.
  • the TEG module is directly flown by the hot and / or cold medium. This means that the prefabricated unit TEG module is located in the flow of the hot exhaust gas and / or the coolant. This prevents heat losses and increases the temperature difference acting on the TEG module.
  • the TEG module with its hot and / or cold side directly from hot or cold fluid, which is guided in a flow channel, flows.
  • the cold medium is in particular a liquid coolant, in particular the coolant of the cooling circuit of the internal combustion engine.
  • the TEG module flows directly from the hot exhaust gas as well as from the liquid coolant, it forms part of the exhaust gas duct wall.
  • the wall has openings in which a TEG module is housed. According to the preferred embodiment, the TEG module is adhered to the wall.
  • the tightness in the region of the opening can be optimized by the fact that the TEG module protrudes laterally relative to the wall and thus rests with this projecting edge on the edge of the opening.
  • An embodiment of the invention provides that a second flow channel is provided, which is spaced from the TEG module. This flow channel is defined by a separate wall on which the TEG module is not seated. The second flow channel allows a portion of the hot exhaust gas or all of the hot exhaust gas to pass therethrough, limiting the amount of heat transferred to the TEG module via the hot exhaust and protecting the TEG module from thermal overload ,
  • the second flow channel forms a bypass, which is selectively flowed through by a control device, in particular by a valve, according to the preferred embodiment.
  • the valve is for example a flap.
  • a device for exhaust heat utilization in internal combustion engines of motor vehicles with a gas-flow-through housing having an inlet for an inlet pipe and an outlet for an outlet pipe, at least one thermoelectric generator module or heat exchanger, the or received in the housing and / or is fixed to the housing, and a control element for influencing the exhaust gas flow within the housing, wherein the inlet and the outlet are connected both via a first flow channel adjacent to the at least one thermoelectric generator module or the heat exchanger and with this heat-conducting is coupled, as well as by a second flow channel, which is spaced from the at least one thermoelectric generator module, wherein the two flow channels are formed in the interior of the housing.
  • the device preferably also has a sound-damping effect.
  • a wall of at least one flow channel has, at least in sections, a gas-permeable surface. Sound insulation material, wherein the wall is preferably coated with the soundproofing material.
  • the soundproofing material may also be formed as a heat shield in this embodiment.
  • the device for exhaust heat utilization Because of the compact design of the device for exhaust heat utilization, it can namely by thermal radiation, for example, then come to a loading of the at least one TEG module or heat exchanger, if only the at least one TEG module or heat exchanger spaced second flow channel is flowed through by the exhaust gas. Due to the advantageous function of the soundproofing material as a heat shield, this undesired effect can be minimized or eliminated, so that the thermal influence of the exhaust gas flow in the second flow channel on the at least one TEG module or the heat exchanger is negligible.
  • the soundproofing material used is preferably a metal foam, a metal mesh or a microperforated wall. All these materials have a sound-damping effect, are simple and inexpensive to produce and have a high heat resistance.
  • the two flow channels are in flow communication via a gas-permeable soundproofing material. As a result, a particularly good sound attenuation can be realized.
  • the soundproofing material preferably has a gas permeability with which a flow resistance between the two flow channels through the soundproofing material is at least a factor of 5 higher than a flow resistance of the individual flow channels from the inlet to the outlet.
  • gas permeability causes excellent sound damping and, on the other hand, ensures that the mass flow between the two flow channels through the soundproofing material is negligible.
  • a tube extends inside the housing, wherein the second flow channel are defined by a tube cross-section and the first flow channel through an annular space between the tube and the housing surrounding the tube. This construction for the formation of two parallel flow channels is extremely compact, easy to manufacture and very inexpensive.
  • the tube is at least partially enclosed by a gas-permeable soundproofing layer.
  • a gas-permeable soundproofing layer This leads, as already mentioned, to an advantageous sound damping in the device and with a formation of the soundproofing layer as a heat shield in addition to a thermal decoupling of the two directly adjacent flow channels.
  • the tube whose tube cross-section defines the first flow channel, can also be perforated in the area of the soundproofing layer.
  • the perforation has a very advantageous effect on the sound attenuation of the device for exhaust heat recovery.
  • At least one TEG module is provided which is heat-conductively attached to the housing.
  • An attachment to the housing can be realized with little effort, allows good heat conduction between the at least one TEG module and the first flow channel and a far-reaching thermal decoupling between the at least one TEG module and the second flow channel.
  • the housing comprises at least two interconnected sheet metal shells. These sheet metal can be stamped with little effort from sheet metal blanks and then formed, resulting in a very inexpensive production of the housing results.
  • each flow channel is formed by an embossed portion of a first sheet metal shell and an embossed portion of a second sheet metal shell.
  • the closed channel cross section can be produced in the simplest way in terms of forming technology.
  • a center axis of the inlet and a center axis of the outlet are aligned in parallel and spaced from one another. standet. This allows easy integration of the device in an exhaust system of the motor vehicle.
  • thermoelectric generator modules are combined to form a flow-through assembly and arranged in the first flow channel, wherein the assembly is transversely, preferably substantially perpendicular to a central axis of the inlet or the outlet can flow.
  • a transverse, preferably substantially perpendicular to a central axis of the inlet or outlet through which a heat exchanger is arranged in the first flow channel is deflected and slowed down, which allows a particularly effective use of thermal exhaust energy through the heat exchanger.
  • the first flow channel may open into the second flow channel downstream of the at least one TEG module or heat exchanger.
  • a cooling circuit is preferably provided which is thermally conductively coupled to the at least one TEG module.
  • a "hot side" of the at least one TEG module with the hot exhaust gas flow and a "cold side” of the at least one TEG module with the cold coolant of the cooling circuit heat-conductively connected so that via the TEG modules a particularly effective conversion of thermal Energy takes place in electrical energy.
  • the control element has a valve flap for influencing the flow components in the first and second flow channels. By regulating the exhaust gas flow in the first flow channel by means of the valve flap, overheating of the TEG modules or the heat exchanger can be reliably prevented.
  • control element is arranged in the region of the inlet at the branch point of the flow channels.
  • control element is arranged on the second flow channel and can close or at least partially release a flow cross-section of the second flow channel.
  • the invention also relates to a thermoelectric generator having a first carrier ceramic associated with a heat source, a second carrier ceramic associated with a heat sink and a plurality of semiconductor elements disposed between the two carrier ceramics.
  • thermoelectric generator more precisely the two carrier ceramics and the semiconductor elements, forms a TEG module in a special design.
  • such a TEG module can be used to convert the temperature difference between the heat source and the heat sink into an electric current. It makes sense to operate the thermoelectric generator either with the temperature difference between the cooling water of the internal combustion engine and the environment or the temperature difference between the exhaust gas and the environment.
  • thermoelectric generator Important for a good efficiency and the highest possible performance of the thermoelectric generator is a good heat transfer to the two carrier ceramics.
  • the TEG module has usually been mechanically clamped, so that the carrier ceramic is pressed, for example on the side of the heat source, against the wall of an exhaust pipe and on the side of the heat sink against a cooling plate.
  • quite high pressures on the order of up to 200 psi are necessary to ensure good heat transfer to the carrier ceramic.
  • the TEG module is directly flown by the cooling fluid or the hot exhaust gas.
  • the TEG module is a prefabricated component which is installed as a whole.
  • the object of the invention is to reduce the effort for the attachment of the TEG module and for maintaining a good heat transfer to the carrier ceramic.
  • the heat source or heat sink is no longer provided as a separate component to the TEG module, but either so far integrated that the carrier ceramic is an integral part of the heat source or the heat sink, or at least cohesively with the heat source or the heat sink is connected.
  • the mechanical separation between the carrier ceramic and the heat source or the heat sink is avoided, which has hitherto required a high mechanical pressure force in order to ensure a good heat transfer.
  • the cohesive connection can be formed in particular by a layer of a solder material. This ensures a very good heat transfer from the heat source or heat sink to the corresponding carrier ceramic.
  • the carrier ceramic is provided with a metal coating, with which the solder material is connected.
  • the metal coating ensures that the solder material makes a good connection.
  • the solder material is an active solder, which is connected directly to the carrier ceramic. Such an active solder avoids the need to first metallize the carrier ceramic before it can be soldered.
  • the cohesive connection can also be formed by a layer of a thermally conductive adhesive.
  • a thermal adhesive ensures a very good heat transfer, which is even better than with solder material.
  • the heat source or heat sink may be a cooling water-conducting component.
  • the engine cooling water heated by the internal combustion engine can serve as a heat source for the TEG module, in which case the ambient temperature serves as a heat sink.
  • the heat source or heat sink is a heat exchanger.
  • Such a heat exchanger for example, be a so-called auxiliary heater for a motor vehicle, with the exhaust gas of the internal combustion engine heat energy can be withdrawn.
  • the heat source is an exhaust gas-carrying component. This makes it possible to use a very large temperature gradient relative to the environment for power generation.
  • a cooling plate can be used, so that comparatively large amounts of heat can be released to the environment with little effort.
  • the carrier ceramic is provided with a plurality of heat transfer ribs. This makes it possible to use the carrier ceramic directly without the interposition of additional components as a heat source or heat sink.
  • the heat transfer hubs may protrude directly into an exhaust pipe of the internal combustion engine.
  • the heat transfer ribs for example, are flowed around by the ambient air.
  • the carrier ceramic is provided with a flow channel. This makes it possible, for example, to guide the heated engine cooling water directly through the carrier ceramic, so that it acts as a heat source without the interposition of other elements. Accordingly high is the thermal efficiency.
  • FIG. 1 is a schematic longitudinal section through an inventive device for exhaust heat recovery according to a first embodiment with the valve flap open;
  • FIG. 2 shows the schematic longitudinal section through the device according to the invention according to FIG. 1 with the valve flap closed;
  • - Figure 3 is a schematic longitudinal section through an inventive device for exhaust heat recovery according to a second embodiment in a flow through the first flow channel;
  • FIG. 4 shows the longitudinal section through the device according to the invention according to Figure 3 at a flow through the second flow channel
  • FIG. 5 is a semi-transparent, perspective view of a flow-through assembly with several TEG modules and integrated cooling;
  • FIG. 6 is a schematic longitudinal section through an inventive device for exhaust heat recovery according to a third embodiment
  • FIG. 7 is a schematic detail section through an exhaust pipe upstream of the inventive device for exhaust heat recovery
  • FIG. 8 shows, in a schematic section, a TEG module according to a fourth embodiment of the invention
  • FIG. 9 is a schematic section of a TEG module according to a fifth embodiment of the invention.
  • FIG. 10 is a schematic section of a TEG module according to a sixth embodiment of the invention.
  • FIG. 11 is a schematic section through a TEG module according to a seventh embodiment of the invention.
  • FIG. 12 is a schematic section through a TEG module according to an eighth embodiment of the invention.
  • FIG. 13 in a schematic section a TEG module according to a ninth embodiment of the invention.
  • Figures 1 to 4 and 6 show a device 10 for exhaust heat utilization in internal combustion engines of motor vehicles, with an exhaust gas flowed through housing 12 having an inlet 14 for an inlet pipe 16 and an outlet 18 for an outlet pipe 20, at least one thermoelectric generator module (TEG Module) 22 or a heat exchanger 24 (cf. gur 6) which is received in the housing 12 and / or fixed to the housing 12, and a control element 26 for influencing the exhaust gas flow 28 within the housing 12.
  • TEG Module thermoelectric generator module
  • a heat exchanger 24 cf. gur 6
  • the inlet 14 and the outlet 18 are both through a first flow channel 30th connected to the at least one TEG module 22 or the heat exchanger 24 and is thermally conductively coupled thereto, as well as by a second flow channel 32, which is spaced from the at least one TEG module 22 or heat exchanger 24, wherein the two flow channels 30, 32 are formed in the interior of the housing 12.
  • Figures 1 and 2 show a first embodiment of the device 10 with a cylindrical cross-sectional structure.
  • the housing 12 is formed by a conical inlet funnel 34, a cylindrical tube section 36 and a conical outlet funnel 38.
  • Inside the housing 12 extends a tube 40, the second flow channel 32 being defined by a tube cross-section and the first flow channel 30 being surrounded by an annular space between tube 40 and housing 12 surrounding the tube 40.
  • control element 26 for influencing the flow components in the first and second flow channels 30, 32.
  • the control element 26 is arranged on the second flow channel 32 in the first embodiment and designed as a valve flap, the valve flap having the flow cross section the second flow channel 32 at least partially release (see Figure 1) or can close (see Figure 2). As shown in the figures, the control element 26 is arranged within the prefabricated unit 10.
  • the device 10 is attached to the inlet tube and the outlet tube 16.
  • the control element 26 lies in particular in the outlet funnel 38. Of course, the control element 26 could also be located in the inlet funnel 34.
  • the control element 26 is located according to Figure 1 in its open position, so that the exhaust stream 28 within the tube 40 from the inlet 14 through the second flow channel 32 can flow to the outlet 18.
  • the exhaust gas stream 28 at the inlet 14 can exit the tube 40 through an opening 42 and flow to the outlet 18 via the first flow channel 30 which is annular in cross-section.
  • the distribution of the exhaust gas flow 28 is determined by the individual flow resistances of the flow channels 30, 32. Simple and suitable measures for influencing the flow resistance are baffles, diaphragms or the like.
  • the flow resistance of the second flow channel 32 in the open position of the control element 26 is significantly lower than the flow resistance of the first flow channel 30.
  • an overheating of the TEG modules 22 be reliably excluded.
  • the second flow channel 32 is essentially sealed except for a negligible leakage flow, so that the entire exhaust gas stream 28 flows from the inlet 14 via the opening 42 through the first flow channel 30 to the outlet 18 of the housing 12.
  • the TEG modules 22 experience their maximum thermal loading by the hot exhaust gas stream 28, which leads to a particularly effective energy conversion and thus to a maximum yield of electrical energy.
  • the control element 26 Only when a limit temperature, with which the TEG modules 22 are allowed to be subjected to a maximum, is reached, the control element 26 at least partially opens the second flow channel 32 in order to avoid overheating and thus damage to the TEG modules 22.
  • a plurality of TEG modules 22 are heat-conductively attached to the housing 12.
  • the TEG modules 22 extend through openings 33 of the pipe section 36 and thus project into both the first flow channel 30 and in the cooling circuit 44.
  • the individual TEG modules 22 at a radial inside of Pipe section 36 are mounted so that they protrude into the first flow channel 30, or on a radial outer side of the pipe section 36 so that they protrude into a cooling circuit 44 indicated only schematically.
  • the numerous TEG modules 22 preferably extend over the entire axial length of the cylindrical part of the pipe section 36.
  • FIGS. 1 and 2 show the housing 12 and / or the TEG modules 22 Heat conducting ribs 47 are provided in order to improve the thermal coupling between the cooling circuit 44 and the TEG modules 22.
  • the heat conduction fins 49 are arranged on the housing 12 and / or on the TEG modules 22, which heat conduction between the exhaust gas stream 28 in the first Improve flow channel 30 and the TEG modules 22.
  • the cooling circuit 44 for cooling the TEG modules 22 may be a separate cooling circuit that cools only the TEG modules 22, or a general cooling circuit (eg engine cooling circuit, air conditioning circuit, etc.), are connected to the still more devices to be cooled ,
  • a gas-permeable soundproofing material 48 can also be seen.
  • the tube 40 is partially enclosed in the axial direction of the soundproofing material 48, in particular coated with the soundproofing material 48, and also perforated in the region of this soundproofing layer.
  • a wall of at least one flow channel 30, 32 at least partially has the gas-permeable soundproofing material 48, preferably coated with this material 48.
  • a particularly suitable soundproofing material 48 is, for example, a metal foam, a metal mesh or a microperforated wall.
  • the soundproofing material 48 further forms a heat shield, which prevents thermal exposure of the TEG modules 22 via thermal radiation of the exhaust gas stream 28 in the second flow channel 32 or at least minimizes it to a negligible extent.
  • the sound attenuation measures in the device 10 have been found to be particularly effective when the two flow channels 30, 32 are in fluid communication via the gas-permeable soundproofing material 48, which is achieved by the perforation 51 of the tube 40 according to Figures 1 and 2.
  • a considerable sound-damping effect arises even when a large part of the exhaust gas stream 28 flows through the second flow channel 32; and this, although the soundproofing material 48 according to Figures 1 and 2 only on a radial outer side of the tube 40, that is, that is arranged in the first flow channel 30.
  • the soundproofing material 48 preferably has a gas permeability with which a flow resistance between the two flow channels 30, 32 through the soundproofing material 48 at least by a factor of 5 is higher than a flow resistance the individual flow channels 30, 32 from the inlet 14 to the outlet 18. In this case, a desired flow resistance between the flow channels 30, 32 with little effort on the density of the soundproofing material 48 and / or the perforation 51 in the tube 40 set.
  • the flow channels 30, 32 are brought together again in the region of the outlet 18. Specifically, while the first flow channel 30 open into the second flow channel 32 to merge the exhaust stream 28 and to introduce into the outlet pipe 20.
  • Figures 3 and 4 show a second embodiment of the device 10 for exhaust heat utilization.
  • the housing 12 is not formed here tubular with approximately circular cylindrical cross-section, but rather cuboid with approximately rectangular cross-section.
  • an axial length and a perpendicular thereto width of the housing 12 is shown. Perpendicular to the plane of the housing 12 extends over a height that is significantly smaller relative to the length and width.
  • the ratio length / height and width / height is at least 2/1, preferably at least 3 / 1.
  • the housing 12 in this case comprises at least two interconnected sheet metal shells 50, one of which can be seen in Figures 3 and 4.
  • a first sheet metal shell 50 forms a bottom part onto which a second sheet metal shell 50 (not shown) acts as a cover part
  • the sheet metal shells 50 are preferably produced as embossing / stamping parts, wherein each flow channel 30, 32 is formed by an embossed section of the first sheet metal shell 50 and an embossed section of the second sheet metal shell 50.
  • the closed cross sections of the flow channels 30 , 32 each by two superimposed, U-shaped embossed Troughs formed in the sheet metal shells 50.
  • the two sheet metal shells 50 may be identical.
  • the inlet 14 and the outlet 18 are disposed at opposite axial ends of the housing 12 with a central axis A of the inlet 14 and a central axis B of the outlet 18 being parallel and spaced from each other.
  • TEG modules 22 can be seen in FIGS. 3 and 4, which are combined to form a flow-through assembly 52 and in the first flow. can be flowed through the assembly 52 substantially perpendicular to the central axis A of the inlet 14 and the central axis B of the outlet 18 (see Figures 3 and 5).
  • Downstream of the flow-through assembly 52 then opens the first flow channel 30 in the region of the outlet 18 in the second flow channel 32, so that the entire exhaust gas stream 28 is introduced into the outlet pipe 20 regardless of the position of the control element 26.
  • control element 26 is also in this case a valve flap for influencing the flow components in the first and second flow channels 30, 32.
  • the control element 26 in the second embodiment is arranged in the area of the inlet 14 at a branch point of the flow channels 30, 32 ,
  • control element 26 deflects the entire exhaust gas stream 28 through the first flow channel 30 and thus through the assembly 52 with the TEG modules 22. This leads to a maximum thermal load on the TEG modules 22 and thus to a maximum electrical energy yield.
  • control element 26 can at least partially direct the exhaust gas stream 28 into the second flow channel 32 acting as a bypass, so that at least part of the exhaust gas stream 28 bypasses the assembly 52. In an extreme position of the control element 26 according to FIG. 4, the entire exhaust gas stream 28 is conducted through the second flow channel 32.
  • Part of the second flow channel 32 directly adjoins the assembly 52, wherein a baffle 54 is provided in this area, which prevents the TEG modules 22 of the assembly 52 from being thermally acted upon by the hot exhaust gas stream 28 in the second flow channel 32 ,
  • FIG. 5 shows a perspective view of the assembly 52, as it is installed in the housing 12 in the second embodiment of the device 10 for utilizing exhaust heat.
  • the TEG modules 22 are arranged in the form of lamellas in the assembly 52, wherein the lamellae extend in the flow direction 56 of the exhaust gas flow 28.
  • FIG. 5 also shows electrical connections 58 of the TEG modules 22, via which the electrical energy obtained can be forwarded to a consumer or a storage medium.
  • cooling coils of the cooling circuit 44 can also be seen, which are thermally coupled to a "cold side" of the TEG modules 22.
  • the cooling coils are formed by tubes which extend out of the assembly 52 on an axial end side and cooling circuit connections 60 These cooling circuit connections 60 are also indicated in Figures 3 and 4 and in Figure 6.
  • This third embodiment is structurally and functionally largely identical to the device 10 according to Figures 3 and 3 4.
  • TEG modules 22 in the first flow channel 30 instead of the TEG modules 22 in the first flow channel 30, a heat exchanger 24 through which the inlet 14 or outlet 18 flows substantially perpendicularly to the center axis A, B is arranged, and consequently the thermal energy of the exhaust stream 28 is not used here TEG modules 22 converted into electrical energy, sond ern over the heat exchanger 24 directly used as heat energy. In this way, the thermal exhaust gas energy can be used, for example, to heat a cooling circuit 44 via the heat exchanger 24. If this cooling circuit 44 is the engine cooling circuit or an air conditioning cooling circuit of the motor vehicle, an improved cold start behavior or a faster heating of the vehicle interior is thereby achieved.
  • FIG. 7 shows a detail of an exhaust pipe 61 upstream of the device 10 for utilizing exhaust heat.
  • This design detail may be integrated into the inlet 14 of the device 10 or the inlet tube 16 in some embodiments.
  • the exhaust pipe 61 in this case has a cross-sectional constriction and supply air openings 62 in the region of the cross-sectional constriction.
  • About the so-called Venturi effect forms in the Area of the supply air openings 62 from a suction effect, which sucks cool ambient air 63 in the exhaust pipe 61.
  • the amount of supplied ambient air 63 can be adjusted in the present case by actuatable flaps 64, which can open or close openings 66 in the outer jacket 68 of the exhaust pipe 61.
  • the TEG modules 22 have to be acted on by the exhaust gas flow 28 as far as possible during the entire operating period of the internal combustion engine.
  • the control element 26 releases the first flow channel 30 in a basic position and blocks the second flow channel 32 (cf., FIGS. 2 and 3), and if, moreover, a spring element is provided which moves the control element 26 into its basic position applied.
  • a spring element is provided which moves the control element 26 into its basic position applied.
  • an active actuation of the control element 26 for releasing the second flow channel 32 is necessary only in the exceptional cases of very high thermal load in order to prevent overheating of the TEG modules.
  • the control element 26 is usually electrically actuated as a function of temperature sensors, for example by an electric motor.
  • Figures 8 to 13 show further embodiments of TEG modules 122 and their arrangement with respect to hot or cold media.
  • FIG. 8 schematically shows a TEG module 122 according to a fourth embodiment, which has a first carrier ceramic 110, a second carrier ceramic 112 and semiconductor elements 114 arranged therebetween.
  • This arrangement uses the so-called Peltier effect and, when there is a temperature difference between the first carrier ceramic 110 and the second carrier ceramic 112, generates a voltage difference. This is well known and will not be discussed further here. For the following exemplary embodiments, Assuming that the first carrier ceramic 110 should be at a higher temperature level during operation than the second carrier ceramic 112.
  • the first carrier ceramic 110 is associated with a heat source, such as an exhaust pipe 116, and the second carrier ceramic 1 12 is a heat sink,
  • a cooling circuit assigned, as it has been previously explained, for example, with reference to Figures 1 to 7.
  • the cooling fluid directly flows to the heat sink 120.
  • the first carrier ceramic 110 is connected to the outer wall of the exhaust pipe 116 by means of a material connection.
  • the cohesive connection here consists of a layer of a solder material 118.
  • a brazing material is preferably used.
  • the solder material 118 may be a so-called active solder, which is suitable for soldering ceramic material.
  • the first carrier ceramic 10 is provided on its outer side with a metallic coating, which then in turn attacks the solder material.
  • the second carrier ceramic 112 is connected to a heat sink 120 by means of a material connection.
  • a heat-conducting adhesive 123 is preferably used here.
  • FIG. 9 shows a fifth embodiment.
  • the same reference numerals are used, and reference is made to the above explanations in this respect.
  • the difference to the fifth embodiment here is that is used as a heat source cooling water K, which comes from an internal combustion engine. This is passed through a heat exchanger 124, which is connected by means of a material connection with the first carrier ceramic. For this purpose, in particular a thermal adhesive 123 can be used again.
  • the heat sink 120 can optionally be directly flowed by hot exhaust gas.
  • FIG. 10 shows a sixth embodiment.
  • the same reference numerals are used, and reference is made to the above explanations in this respect.
  • the heat sink 120 can optionally be flowed directly by hot exhaust gas so that the heat sink 120 forms a section of the wall of the exhaust gas duct.
  • the difference between the fifth and sixth embodiments is that in the sixth embodiment, the cooling water K is directly passed through the first carrier ceramic 110. This is provided for this purpose with at least one flow channel 126. In this way, the heat transfer from the heat exchanger 124 to the first carrier ceramic 110, as it is present in the embodiment of FIG. 8, is eliminated.
  • FIG. 11 shows a seventh embodiment.
  • the seventh embodiment differs from the fourth embodiment in that the second carrier ceramic 1 12 is provided with a plurality of heat transfer ribs 128, so that it itself acts directly as a heat sink. This eliminates the heat transfer from the second carrier ceramic 112 to the heat sink 120, as it is present in the embodiment of Figure 7. Again, cooling fluid can flow directly to the ribs 126.
  • Fig. 12 an eighth embodiment is shown. For the components known from the preceding embodiments, the same reference numerals are used, and reference is made to the above explanations in this respect.
  • the first carrier ceramic 1 10 is provided with heat transfer ribs 128, which project through an opening 130 in the exhaust pipe 116 into the interior of the exhaust pipe.
  • the carrier ceramic 110 is heated directly from the hot exhaust gas stream, and it eliminates the heat transfer from the exhaust pipe 1 16 to the first carrier ceramic 1 10, as it is present in the fourth embodiment.
  • a heat sink 120 is used, which is formed as a flat sheet.
  • Fig. 13 a ninth embodiment is shown.
  • the same reference numerals are used for the components known from the preceding embodiments, and reference is made to the above explanations in this respect.
  • the second carrier ceramic 1 12 is formed as a heat exchanger and is provided for this purpose with a flow channel 126.
  • a forced cooling of the second carrier ceramic 112 by means of a suitable coolant which hits directly on the TEG module.
  • the TEG module is also directly flowed into the hot exhaust gas, because it forms part of the channel wall for the exhaust gas and closes an opening 130 in the exhaust pipe 1 16.
  • the TEG module is laterally opposite this over (see Figures 12 and 13) better sealing and fastening.
  • an elastic compensation element between the inner wall of the housing and the components, which causes a clamping in the housing.
  • a bearing or fiber mat can be used as the elastic compensating element, as used, for example, as a clamping and compensating element in the fixation of catalyst substrates.
  • the mat may for example consist of a knitted fabric or knit fabric, eg made of a steel wire.
  • Canning method For mounting in the housing, one of the known from the production of catalyst or particulate filter modules Canning method can be used, for example, winding, plugging or calibrating, in which the necessary clamping force is generated on the components by a targeted deformation of the housing.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Exhaust Silencers (AREA)

Abstract

L'invention concerne un dispositif pour l'utilisation de la chaleur des gaz d'échappement dans des moteurs à combustion interne de véhicules automobiles qui comprend au moins un module TEG (22) avec un côté chaud et un côté froid, le côté chaud et/ou le côté froid étant en contact fluidique direct avec un fluide chaud ou froid. En outre, le dispositif présente un boîtier parcouru par les gaz d'échappement, qui présente une entrée pour un tube d'admission et une sortie pour un tube d'échappement, le module TEG ou un échangeur de chaleur étant reçu dans le boîtier, et un élément de commande pour influencer le flux de gaz d'échappement à l'intérieur du boîtier. L'entrée et la sortie sont reliées à la fois par un premier canal d'écoulement, qui est adjacent à l'au moins un module de générateur thermoélectrique ou à l'échangeur de chaleur, et est accouplé à celui-ci avec conduction de la chaleur, et aussi par un deuxième canal d'écoulement, qui est espacé de l'au moins un module de générateur thermoélectrique ou de l'échangeur de chaleur, les deux canaux d'écoulement étant réalisés à l'intérieur du boîtier.
PCT/EP2011/001051 2010-03-03 2011-03-03 Dispositif pour l'utilisation de la chaleur des gaz d'échappement WO2011107282A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE202010003049.8 2010-03-03
DE202010003049U DE202010003049U1 (de) 2010-03-03 2010-03-03 Vorrichtung zur Abgaswärmenutzung
DE202010007872.5 2010-06-11
DE202010007872U DE202010007872U1 (de) 2010-06-11 2010-06-11 Thermoelektrischer Generator

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WO2013068291A1 (fr) * 2011-11-11 2013-05-16 Friedrich Boysen Gmbh & Co. Kg Dispositif de conversion d'une énergie calorifique en énergie électrique
CN103147879A (zh) * 2013-03-12 2013-06-12 武汉理工大学 一种汽车尾气温差发电热交换器
WO2014001337A1 (fr) * 2012-06-29 2014-01-03 Elringklinger Ag Dispositif de blindage thermique à utilisation d'énergie thermo-électrique
EP2716886A1 (fr) * 2012-10-08 2014-04-09 Rolls-Royce plc Dispositif d'échappement
FR3011205A1 (fr) * 2013-09-30 2015-04-03 Renault Sa Dispositif de generation d'electricite pour vehicule comportant un moteur thermique
FR3022075A1 (fr) * 2014-06-04 2015-12-11 Valeo Systemes Thermiques Elements, module et dispositif thermo electrique, notamment destines a generer un courant electrique dans un vehicule automobile
EP3012428A1 (fr) * 2014-10-24 2016-04-27 Valeo Systemes Thermiques Module thermo électrique, notamment destinés à générer un courant électrique dans un véhicule automobile
CN106050375A (zh) * 2016-08-02 2016-10-26 清华大学苏州汽车研究院（相城） 一种适用于尾气热电回收的排气消声器
WO2016193453A1 (fr) 2015-06-05 2016-12-08 Bombardier Transportation Gmbh Générateur thermoélectrique pour convertir la chaleur d'un flux de gaz chaud en énergie électrique
FR3041162A1 (fr) * 2015-09-15 2017-03-17 Valeo Systemes Thermiques Dispositif thermo electrique, notamment destine a generer un courant electrique dans un vehicule automobile
GB2549123A (en) * 2016-04-06 2017-10-11 Jaguar Land Rover Ltd Energy recovery unit for vehicle use
GB2549124A (en) * 2016-04-06 2017-10-11 Jaguar Land Rover Ltd Energy recovery unit for vehicle use
US20180149112A1 (en) * 2016-11-29 2018-05-31 Mahle International Gmbh Heat exchanger for a motor vehicle
US20180149062A1 (en) * 2016-11-29 2018-05-31 Mahle International Gmbh Heat exchanger for a motor vehicle
EP3404227A1 (fr) 2017-05-16 2018-11-21 Magneti Marelli S.p.A. Générateur thermoélectrique pour un système d'échappement d'un moteur à combustion interne
CN109075244A (zh) * 2016-04-06 2018-12-21 捷豹路虎有限公司 车用能量回收单元
EP3503229A1 (fr) 2017-12-20 2019-06-26 Magneti Marelli S.p.A. Intercooler avec un générateur thermoélectrique pour un moteur à combustion interne à charge turbo
US20190234277A1 (en) * 2018-01-30 2019-08-01 Jaguar Land Rover Limited Fluid flow network for a vehicle
IT201800010501A1 (it) 2018-11-22 2020-05-22 Magneti Marelli Spa Metodo di controllo di un generatore termoelettrico per un motore a combustione interna
IT201900012405A1 (it) 2019-07-19 2021-01-19 Magneti Marelli Spa Convertitore elettronico dc-dc per pilotare un generatore termoelettrico per un motore a combustione interna

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Cited By (34)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013068291A1 (fr) * 2011-11-11 2013-05-16 Friedrich Boysen Gmbh & Co. Kg Dispositif de conversion d'une énergie calorifique en énergie électrique
WO2014001337A1 (fr) * 2012-06-29 2014-01-03 Elringklinger Ag Dispositif de blindage thermique à utilisation d'énergie thermo-électrique
EP2716886A1 (fr) * 2012-10-08 2014-04-09 Rolls-Royce plc Dispositif d'échappement
US9016048B2 (en) 2012-10-08 2015-04-28 Rolls-Royce Plc Exhaust arrangement
CN103147879A (zh) * 2013-03-12 2013-06-12 武汉理工大学 一种汽车尾气温差发电热交换器
FR3011205A1 (fr) * 2013-09-30 2015-04-03 Renault Sa Dispositif de generation d'electricite pour vehicule comportant un moteur thermique
FR3022075A1 (fr) * 2014-06-04 2015-12-11 Valeo Systemes Thermiques Elements, module et dispositif thermo electrique, notamment destines a generer un courant electrique dans un vehicule automobile
EP3012428A1 (fr) * 2014-10-24 2016-04-27 Valeo Systemes Thermiques Module thermo électrique, notamment destinés à générer un courant électrique dans un véhicule automobile
FR3027734A1 (fr) * 2014-10-24 2016-04-29 Valeo Systemes Thermiques Module thermo electrique, notamment destines a generer un courant electrique dans un vehicule automobile
CN107709720A (zh) * 2015-06-05 2018-02-16 庞巴迪运输有限公司 用于将热气体流的热转换成电能的热电发生器
US20180149061A1 (en) * 2015-06-05 2018-05-31 Bombardier Transportation Gmbh Thermoelectric Generator for Converting Heat of a Hot Gas Flow Into Electric Energy
DE102015210398A1 (de) 2015-06-05 2016-12-08 Bombardier Transportation Gmbh Thermoelektrischer Generator zur Umwandlung von Wärme eines heißen Gasstroms in elektrische Energie
WO2016193453A1 (fr) 2015-06-05 2016-12-08 Bombardier Transportation Gmbh Générateur thermoélectrique pour convertir la chaleur d'un flux de gaz chaud en énergie électrique
FR3041162A1 (fr) * 2015-09-15 2017-03-17 Valeo Systemes Thermiques Dispositif thermo electrique, notamment destine a generer un courant electrique dans un vehicule automobile
WO2017046488A1 (fr) * 2015-09-15 2017-03-23 Valeo Systemes Thermiques Dispositif thermo électrique, notamment destiné a générer un courant électrique dans un véhicule automobile
US10823111B2 (en) 2016-04-06 2020-11-03 Jaguar Land Rover Limited Energy recovery unit for vehicle use
GB2549123B (en) * 2016-04-06 2019-10-09 Jaguar Land Rover Ltd Energy recovery unit for vehicle use
CN109075244B (zh) * 2016-04-06 2022-06-28 捷豹路虎有限公司 车用能量回收单元
GB2549124A (en) * 2016-04-06 2017-10-11 Jaguar Land Rover Ltd Energy recovery unit for vehicle use
US11289636B2 (en) 2016-04-06 2022-03-29 Jaguar Land Rover Limited Energy recovery unit for vehicle use
GB2549123A (en) * 2016-04-06 2017-10-11 Jaguar Land Rover Ltd Energy recovery unit for vehicle use
CN109075244A (zh) * 2016-04-06 2018-12-21 捷豹路虎有限公司 车用能量回收单元
GB2549124B (en) * 2016-04-06 2019-06-05 Jaguar Land Rover Ltd Energy recovery unit for vehicle use
CN106050375A (zh) * 2016-08-02 2016-10-26 清华大学苏州汽车研究院（相城） 一种适用于尾气热电回收的排气消声器
CN108120317A (zh) * 2016-11-29 2018-06-05 马勒国际有限公司 热交换器，尤其是用于机动车辆的排气热交换器
US20180149062A1 (en) * 2016-11-29 2018-05-31 Mahle International Gmbh Heat exchanger for a motor vehicle
US20180149112A1 (en) * 2016-11-29 2018-05-31 Mahle International Gmbh Heat exchanger for a motor vehicle
EP3404227A1 (fr) 2017-05-16 2018-11-21 Magneti Marelli S.p.A. Générateur thermoélectrique pour un système d'échappement d'un moteur à combustion interne
EP3503229A1 (fr) 2017-12-20 2019-06-26 Magneti Marelli S.p.A. Intercooler avec un générateur thermoélectrique pour un moteur à combustion interne à charge turbo
US10865702B2 (en) 2017-12-20 2020-12-15 Marelli Europe S.P.A. Intercooler provided with a thermoelectric generator for a turbocharged internal combustion heat engine
US20190234277A1 (en) * 2018-01-30 2019-08-01 Jaguar Land Rover Limited Fluid flow network for a vehicle
US10920643B2 (en) * 2018-01-30 2021-02-16 Jaguar Land Rover Limited Fluid flow network for a vehicle including flow members that respond to a flow imbalance
IT201800010501A1 (it) 2018-11-22 2020-05-22 Magneti Marelli Spa Metodo di controllo di un generatore termoelettrico per un motore a combustione interna
IT201900012405A1 (it) 2019-07-19 2021-01-19 Magneti Marelli Spa Convertitore elettronico dc-dc per pilotare un generatore termoelettrico per un motore a combustione interna

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