Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P3/00—Liquid cooling
  • F01P3/18—Arrangements or mounting of liquid-to-air heat-exchangers
• • 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
  • F02M26/24—Layout, e.g. schematics with two or more coolers
• • 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
  • F02M26/31—Air-cooled heat exchangers
• • 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
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P3/00—Liquid cooling
  • F01P3/18—Arrangements or mounting of liquid-to-air heat-exchangers
  • F01P2003/182—Arrangements or mounting of liquid-to-air heat-exchangers with multiple heat-exchangers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P3/00—Liquid cooling
  • F01P3/18—Arrangements or mounting of liquid-to-air heat-exchangers
  • F01P2003/185—Arrangements or mounting of liquid-to-air heat-exchangers arranged in parallel
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P5/00—Pumping cooling-air or liquid coolants
  • F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
  • F01P5/04—Pump-driving arrangements
  • F01P2005/046—Pump-driving arrangements with electrical pump drive
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P2060/00—Cooling circuits using auxiliaries
  • F01P2060/02—Intercooler
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P2060/00—Cooling circuits using auxiliaries
  • F01P2060/16—Outlet manifold
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P5/00—Pumping cooling-air or liquid coolants
  • F01P5/02—Pumping cooling-air; Arrangements of cooling-air pumps, e.g. fans or blowers
  • F01P5/08—Use of engine exhaust gases for pumping cooling-air
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P7/00—Controlling of coolant flow
  • F01P7/02—Controlling of coolant flow the coolant being cooling-air
  • F01P7/026—Thermostatic control
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
  • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
  • F01P7/00—Controlling of coolant flow
  • F01P7/02—Controlling of coolant flow the coolant being cooling-air
  • F01P7/08—Controlling of coolant flow the coolant being cooling-air by cutting in or out of pumps
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B29/00—Engines characterised by provision for charging or scavenging not provided for in groups F02B25/00, F02B27/00 or F02B33/00 - F02B39/00; Details thereof
  • F02B29/04—Cooling of air intake supply
  • F02B29/0406—Layout of the intake air cooling or coolant circuit
  • F02B29/0437—Liquid cooled heat exchangers
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B33/00—Engines characterised by provision of pumps for charging or scavenging
  • F02B33/32—Engines with pumps other than of reciprocating-piston type
  • F02B33/34—Engines with pumps other than of reciprocating-piston type with rotary pumps
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
  • F02B37/005—Exhaust driven pumps being combined with an exhaust driven auxiliary apparatus, e.g. a ventilator
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
  • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
  • F02B37/00—Engines characterised by provision of pumps driven at least for part of the time by exhaust
  • F02B37/013—Engines characterised by provision of pumps driven at least for part of the time by exhaust with exhaust-driven pumps arranged in series
• • 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

Definitions

• the invention relates to a cooling system for a motor vehicle according to the preamble of claim 1.
• the fundamental problem with exhaust gas recirculation is that the engine's engine performance and pollutant emissions are better, the cooler the intake-side gases are.
• the cooling of the recirculated exhaust gases by means of a liquid heat exchanger to principle limits, since the temperature of the cooling secondary medium is in the range of 100 0 C, at least when using main engine coolant.
• DE 102 03 003 A1 describes a cooling system for a motor vehicle, in which a part of the exhaust gases of the internal combustion engine are introduced into a charged fresh air flow, wherein the recirculated exhaust gases are previously cooled by a liquid-heat exchanger provided with a bypass.
• the liquid heat exchanger is connected to the main cooling circuit of the internal combustion engine. It is the object of the invention to improve a cooling system for an internal combustion engine with regard to its overall thermal performance.
• the cooling system for a motor vehicle comprises a first substantially arranged in the front of the vehicle heat exchanger, which is in particular designed as a main cooler, for cooling a coolant that is particularly liquid and / or gaseous, an internal combustion engine by an air flow of ambient air, and, if necessary, additional heat exchanger for Cooling or heating of other media includes and a second cooler, which is cooled by an air flow of ambient air.
• the second radiator is arranged spatially separated from the main radiator, wherein the air flow for the second radiator and the air flow for the main radiator are spatially separated from each other from the environment.
• the second radiator advantageously the direct cooling of gases, in particular of exhaust gas and / or charge air, is used.
• the cooling system comprises an air conveying means by means of which the second radiator is wetted with an air flow of ambient air, wherein the air conveying means is in particular a relative to a main fan of the first heat exchanger air conveying means.
• the air conveyor is a radial fan.
• Radial fans are particularly pressure-resistant and particularly uncritical with regard to the Angle of incoming and outgoing air.
• radial fans are particularly suitable for supplying a second radiator according to the invention, if the second radiator and / or the air intake is disposed at an unfavorable position in the engine compartment, especially if an angled air duct in the region of the air conveyor is required.
• radial fans provide a high flow rate with limited space and relatively low noise.
• an axial fan can also be used as an air conveyor.
• this may preferably be arranged before the second cooler (pressure operation), but also after the second cooler (suction operation). Furthermore, the air conveyor can also be arranged between two coolers.
• the air conveyor is driven by an electric motor.
• the air conveyor may also be mechanically coupled to the internal combustion engine, in particular via a coupling agent.
• any type of power transmission can be given to the air conveyor, for example, a hydrostatic drive.
• the air conveying means is designed drivable via an exhaust gas turbine. It may be a separate, only the drive of the air conveyor associated exhaust gas turbine.
• the air conveyor with a shaft of an exhaust gas turbocharger for air charging can be driven.
• the air conveying means may be a paddle wheel applied to a protruding pin of the exhaust gas turbocharger shaft, wherein a corresponding further housing part is added to the exhaust gas turbocharger.
• the exhaust gas turbocharger can be modular, so that it can also be used as a component without the additional air conveyor in corresponding vehicles, with a modified version with additional Air conveyor module may be used in other engines with, for example, higher emission limits or higher power.
• a drive of the air conveyor can be controlled in a selectable manner, in particular switched on and off, is formed. In this way, the energy consumption can be reduced according to the driving situation, if no drive of the air conveyor of the second radiator is required.
• a third cooler is provided, which is flowed through by the internal combustion engine supplied gas, wherein the gas in the third cooler by means of a liquid medium, in particular a coolant of the internal combustion engine, can be cooled.
• a liquid medium in particular a coolant of the internal combustion engine
• the second radiator is flowed through by a recirculated to the internal combustion engine exhaust gas stream.
• the second radiator may be a low-pressure exhaust gas cooler in which the exhaust gas carried in the radiator is removed after a final stage of an exhaust gas turbocharger system.
• the second cooler can also be flowed through by a stream of charged fresh air guided to the internal combustion engine, or in a further alternative embodiment by a mixture of charged fresh air and exhaust gas routed to the internal combustion engine.
• this is advantageously a parallel flow cooler, in particular a countercurrent cooler. Due to the parallel flow arrangement, the fact is taken into account that in the majority of cases the second cooler is to be accommodated in limited and possibly unfavorably shaped space.
• the countercurrent arrangement is particularly advantageous in terms of cooling capacity.
• the design of the second cooler may be a tri-flow cooler in which three connections are provided for the cooling secondary medium, which leads to a particularly good combination of cooling capacity and temperature distribution in the material of the cooler.
• the second cooler can also be an at least two-pass cooler, as a result of which the cooling capacity can be improved for a given cooler dimension and sufficient cooling air flow available.
• the second cooler may also be a cross-flow cooler.
• a further air-cooled radiator is provided, wherein the second radiator for cooling of one of the two, exhaust or fresh charge air, and the further radiator is designed for cooling of the other of the two.
• both air-cooled radiators may be spatially separated from a main radiator of the vehicle, but it may also be present only one of the two air-cooled radiator in a spatially separate arrangement to the main radiator.
• a stream of ambient air can be conveyed through a common air conveyor to both the second and the further radiator. This can be realized, for example, in that the second radiator and the further radiator are arranged adjacent.
• the air flow assigned to the second cooler can be changed in size by means of a valve means, in particular an adjustable flap.
• a valve means in particular an adjustable flap.
• a variable branch in particular a bypass, may be provided in front of the second radiator.
• air-cooled gas cooler can freeze at low outdoor temperatures, with frozen condensed water of the guided gases, especially in the case of guided exhaust gases, can reduce or prevent the passage of the primary medium through the radiator.
• the variable branch can be either a bypass or simply an opening, by means of which jammed exhaust gas is blown into the environment.
• the variability of the branch can consist in a pressure relief valve or in an adjustable flap.
• the arrangement is designed so that the heat exchanger is heated by blowing or bypass diversion of the gas to melt the frozen condensed water.
• the outflowing cooling air of the second radiator is at least partially fed to a vehicle interior for purposes of heating.
• provision can be made, for example, for an admission of the cooling air flowing out from the second radiator via a duct into an inlet area of a ventilating or also air-conditioning system of the vehicle.
• the supply of the heated exhaust air can be controlled for example via a valve.
• a considerable advantage of such use of the heated cooling air lies in a particularly quick response of the vehicle heating system when the engine is cold-starting.
• the second radiator will often be arranged in a lateral or rear area of the engine compartment, resulting in a better connection possibility of the exhaust air flow to the ventilation system compared to the main radiator.
• intake of ambient air for cooling the second radiator takes place outside of the engine compartment.
• an intake can be provided in the region of a wheel house.
• FIG. 1 shows a schematic representation of a first exemplary embodiment of a cooling system according to the invention.
• Fig. 2 shows a schematic representation of a second embodiment of a cooling system according to the invention.
• Fig. 3 shows a schematic representation of a third embodiment of a cooling system according to the invention.
• 4 shows a schematic illustration of a fourth exemplary embodiment of a cooling system according to the invention.
• Fig. 5 shows a schematic representation of a countercurrent, parallel flowed through heat exchanger.
• Fig. 6 shows a schematic representation of a tri-flow cooler.
• Fig. 7 shows a schematic representation of a 2-path cooler.
• Fig. 8 shows a schematic representation of a cross-flow cooler.
• the inventive cooling system according to FIG. 1 (first exemplary embodiment) comprises a main radiator 1 of an internal combustion engine 2, which cools the internal combustion engine 2 in a manner known per se via a liquid coolant in a closed cooling circuit 3.
• the main radiator 1 is arranged in the front region of the vehicle and is at least largely traversed by driving wind.
• a main fan 4 is provided in sucking arrangement on the main radiator 1, by means of which a sufficient ensuring adequate air flow through the main radiator even at low speeds.
• the internal combustion engine 2 has a charge of its supplied fresh gas 6 by means of an exhaust gas turbocharger 5, wherein the charged fresh air 6 must be cooled before being supplied to the internal combustion engine 2 due to the heating generated in the exhaust gas turbocharger 5.
• one of the main radiator 1 spatially separate charge air cooler 7 is provided, which is a second radiator in the context of the invention.
• the charge air cooler 7 is flown by means of an air conveyor 8 designed as an electric fan with ambient air 9, whereby a direct cooling of the charge air 6 is provided in an open cooling circuit.
• the spatial arrangement of the components in FIG. 1 also shows that the intercooler 7 and the air conveyor 8 are not arranged in the front area of the vehicle, but in a lateral engine compartment area. Due to the fostanordung in the air stream area, the air conveyor 8 will be regularly in operation when the intercooler 7 must be operated with sufficient cooling capacity.
• a partial exhaust gas recirculation is provided via a branch 10 in the exhaust pipe of the internal combustion engine 2, wherein in one via a valve (not shown) controllable interface 11, a merger of the exhaust gas is carried out with the charged fresh air.
• the recirculated exhaust gas is cooled in a third cooler 12 before merging in the region 10.
• the third radiator 12 is arranged in the main cooling circuit of the internal combustion engine 2 in parallel with the internal combustion engine 2, so that the dissipated heat of the exhaust gas is finally introduced via the liquid-cooled third radiator 12 into the main coolant of the internal combustion engine 2.
• the heat flows in the cooling system of the internal combustion engine 2 are such that, due to the exhaust gas recirculation, less heat energy is given to the outside by the exhaust gas or more heat energy in the internal combustion engine Coolant is registered.
• the additional amount of heat introduced into the coolant is dissipated by a larger than usual designed main cooler. Due to the larger design of the main radiator 1 is not known per se combination of the main radiator with a charge air cooler to a module or makes sense of the cooling performance ago. Therefore, the intercooler 7 is arranged separately and charged with ambient air, which is driven by an air conveyor 8.
• the heat balance according to the embodiment of the invention is such that the amount of heat that is removed from the exhaust, essentially via the intercooler 7 in addition to the Ambient air is discharged.
• the second exemplary embodiment according to FIG. 2 differs from the first exemplary embodiment mainly in that a further exhaust gas cooler 13 surrounded by ambient air and spatially separated from the main cooler 1 is provided, which in the flow direction of the recirculated exhaust gas is the liquid-cooled first exhaust gas cooler (or third cooler) 12 is downstream. This makes sense in terms of cooling the exhaust gas, since the ambient air temperature is regularly below the coolant temperature.
• the exhaust gas cooler 13 and intercooler 7 may be arranged directly adjacent to each other and flow around the same fresh air stream, or they may be arranged spatially separated, for which purpose air ducts are mostly separate from the branch 14 to the supply line the fresh air to the respective radiators 7, 13 are provided.
• the main radiator 1 is designed to be particularly large, as in the first embodiment, in order to avoid the additional heat memege, which is introduced through the liquid-cooled exhaust gas cooler 12 into the circuit of the internal combustion engine 2, wherein in addition amount of heat from both the air-flow intercooler 307 and the air flowing around the exhaust gas cooler 13 is discharged directly to the environment.
• the cooling system according to the third preferred embodiment has an intercooler 307 which, in contrast to the first and second embodiments, is not arranged spatially separate from the main radiator 1, but is combined with it in a manner known per se to form an assembly , As a result, the intercooler 307 is surrounded by the same as the main radiator 1 by the wind and therefore requires a reduction in the possible cooling capacity of the main radiator 1.
• the first stage is also achieved by a third cooler 12 and the second stage by an air-cooled heat exchanger 13.
• the heat exchanger 13 is flowed around by pumped fresh air, wherein a conveying means 308 is provided for the ambient air or fresh air.
• the fan 308c may also be placed directly on a shaft of the exhaust gas turbocharger 5, in order to save components and installation space.
• the exhaust gas turbocharger has a module-like further housing part for forming the air conveying means (not shown).
• the cooling system according to a fourth preferred embodiment has similarities with that of the third embodiment. Deviating, however, there is a two-stage supercharging of the internal combustion engine 2 with a first exhaust gas turbocharger 5 a and a second exhaust gas turbocharger 5 b, which are arranged serially one behind the other. After a first The charging stage of the fresh air through the second exhaust gas turbocharger 5 b is a luftumströmter intercooler 415 is provided which cools the pre-compressed charge air before entering the compressor stage of the first exhaust gas turbocharger 5a and is finally compressed there.
• the intercooler 415 can serve as a "second cooler” or as “another cooler” in the context of the invention.
• the compressed charge air flows through the main charge air cooler 407, which in principle is known from the third exemplary embodiment and is unified with the main radiator 1 to form a structural unit, after which recirculated exhaust gas is fed to the final-dense and cooled charge air at an interface 11.
• the recirculated exhaust gas is, as in the third exemplary embodiment, cooled in two stages via a liquid-cooled second cooler 12 and an air-cooled cooler 13.
• two air-cooled gas coolers 415, 13 which are arranged spatially separated from the main radiator 1 and the main charge air cooler 407 in the engine compartment, thus fail in the fourth exemplary embodiment.
• an electrically operated and designed as a radial fan air conveyor 8 is provided, which presses in an oppressive arrangement air through a branch 414, through which the cooling air is distributed to the two coolers 13, 415.
• an adjustable valve or an adjusting flap 416 is provided in the supply channel to the cooler 13. By regulating this valve 416, a regulated distribution of the cooling air flow to the two coolers 13, 415 can be set. This makes it possible to optimize the cooling system depending on the operating state.
• a total of four coolers 1, 13, 407, 415 are provided which effect a direct open cooling with ambient air and thus deliver heat generated by the internal combustion engine 2 into the environment.
• FIGS. 5 to 8 show exemplary schematic embodiments of heat exchangers which are particularly suitable in terms of their construction for a second cooler according to the invention or else a further cooler.
• FIG. 5 shows a parallel flow, operated in countercurrent heat exchanger 501, which in a direction of a primary medium 20th and in a separate chamber in the opposite direction of a cooling air flow 21 (secondary medium) is flowed through.
• FIG. 6 shows a tri-flow cooler, 601, which is flowed through in one direction by the primary medium 20 to be cooled.
• cooling air is supplied to the two end-side nozzle 602, 604 and discharged through the central port 603.
• the cooling air thus flows rectified with the primary medium and in the subsequent second section opposite to the primary medium. This makes it possible to increase the cooling capacity with sufficient available amount of cooling air 21 and given dimensions, in particular, with a uniform heating of the radiator 601 is given.
• the cooling capacity can be optimized by a two-path cooler 701 (see Fig. 7) with the cooling air 21 via and four ports 702, 703, 704, 705 provided on the cooler, respectively exit, wherein two counter-current cooling paths are provided sequentially along the path of the primary medium 20.
• a crossflow cooler 801 is easy to manufacture and effective if the required space is available.
• a second cooler in the sense of the invention may have a tube bundle construction in construction, in particular with air-cooled ribbing. It may also be a disk construction with axial flow through the primary gas, in particular with double-sided ribbing, in particular with a surrounding housing. Alternatively, a second cooler may have a disk construction in which the primary medium flows across the disks transversely; Again, there may be a ribbing. Both the primary side and the secondary side can each be configured with turbulence generators (winglets) or also inside-ribbed. Quite generally, it can be provided in each of the exemplary embodiments described that the fresh air heated by the cooling process is not or only partially dissipated into the environment and used for heating the interior of the vehicle. This can be done via admixture or by means of a heat exchanger. For this purpose, not shown cooling air ducts and control valves can be used in a simple manner.
• the optionally released installation space can also be used to implement an additional low-temperature coolant circuit in addition to the main coolant circuit, with a second coolant cooler arranged largely in front of the main coolant cooler on the vehicle front side.
• a refrigerant circuit instead of a low-temperature coolant circuit, it is also possible to provide a refrigerant circuit, wherein instead of the second coolant cooler, a condenser is arranged substantially in front of the coolant radiator.
• the cooling air can heat up strongly, measures can be provided at the outlet of the cooling air into the environment in order to prevent the inadmissible heating of other vehicle components or endangerment of persons, especially passers-by. This can be done by a suitable positioning of the outlet, in particular above the driver's cab, for example. It can also be advantageous to dispense the cooling air via the exhaust.
• the cooling air at the outlet can be mixed with ambient air and thus cooled. Particularly useful in this case may be a strong turbulence of the cooling air at the outlet, in particular, the application of strong swirl is to call the particularly effective for breaking the escaping gas jet and thus more efficient mixing with ambient air leads.

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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-Gas Circulating Devices (AREA)
• Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
• Motor Or Generator Cooling System (AREA)

Applications Claiming Priority (2)

Publications (2)

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Family Cites Families (40)

• 2005
  • 2005-09-06 DE DE102005042396A patent/DE102005042396A1/de not_active Withdrawn
• 2006
  • 2006-09-06 US US12/065,678 patent/US8028522B2/en not_active Expired - Fee Related
  • 2006-09-06 JP JP2008528439A patent/JP2010502870A/ja active Pending
  • 2006-09-06 WO PCT/EP2006/008682 patent/WO2007028591A2/fr active Application Filing
  • 2006-09-06 EP EP06805656A patent/EP1926895B1/fr not_active Not-in-force
  • 2006-09-06 CN CN2006800325863A patent/CN101263285B/zh not_active Expired - Fee Related
  • 2006-09-06 AT AT06805656T patent/ATE556205T1/de active

Non-Patent Citations (1)

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