US20080087402A1

US20080087402A1 - Apparatus for cooling charge air for a combustion engine, system with an apparatus for cooling charge air

Info

Publication number: US20080087402A1
Application number: US11/870,172
Authority: US
Inventors: Roland Burk
Original assignee: Behr GmbH and Co KG
Current assignee: Mahle Behr GmbH and Co KG
Priority date: 2006-10-11
Filing date: 2007-10-10
Publication date: 2008-04-17
Also published as: EP1911946A2; DE102006048485A1; EP1911946A3; EP1911946B1

Abstract

A device for charge-air cooling for an internal combustion engine (13) of a motor vehicle, having at least one first heat exchanger (9) for charge-air cooling with at least one first flow duct (7) for a throughflow of a first medium which is to be cooled, with at least one second flow duct (8) for a throughflow of first medium which is substantially not to be cooled, and with at least two third flow ducts (6) for a throughflow of a coolant and/or refrigerant, having at least one housing (2) for holding the at least one first heat exchanger (9), wherein at least one regulating device (4) for temperature regulation and uniform temperature mixture of the first medium after flowing through the first heat exchanger (9) is provided.

Description

In order to increase the power density of internal combustion engines and in order to improve the consumption and emission behavior, the air which is sucked in by the internal combustion engine is charged in a single-stage or multi-stage process by means of at least one compressor, in particular turbocharger, or in the case of multi-stage charging, by means of a plurality of compressors, in particular turbochargers. During charging, the charge air is heated, and as a result, the charge air must be cooled again by means of one or by means of a plurality of charge-air cooling stages after charging.
A further means for reducing the emissions of the internal combustion engine is the exhaust-gas cooling of recirculated exhaust gas; here, a part of the exhaust gas is cooled, in particular in one or in a plurality of exhaust-gas heat exchangers, and is subsequently supplied back to the engine, in particular to the charge air.
Multi-stage cooling of the charge air is known in which at least one cooling stage is an evaporator which is connected to the refrigeration circuit of an air-conditioning system. Here, the evaporator for charge-air cooling is preferably arranged as close as possible to or in the air distributor in order in particular to prevent a re-heating of the charge air on account of the high engine temperature.
U.S. Pat. No. 5,269,143 discloses a cooling system for cooling charge air, which cooling system is arranged in the interior of an internal combustion engine. The system has a two-stage turbocharger subsystem with two compressors which are driven by turbines and which are arranged in series with two intermediate coolers and a refrigerant subsystem.
A device for cooling charge air is also known from EP1342893.
It is an object of the present invention to design more cost-effectively and to improve a device for charge-air cooling for an internal combustion engine of the type specified in the introduction, and in particular to prevent or reduce temperature stranding of the cooled medium, in particular of the charge air.
Said object is achieved by means of the features of claim 1.
Proposed is a device for charge-air cooling for an internal combustion engine, having at least one first heat exchanger for charge-air cooling with at least one first flow duct for a throughflow of a first partial flow of a first medium, with at least one second flow duct for a throughflow of a second partial flow of the first medium, and with at least one third flow duct for a throughflow of a coolant and/or refrigerant, with the first flow duct being thermally connected to the at least one third flow duct, and the at least one second flow duct being thermally insulated, wherein at least one regulating device for temperature regulation and uniform temperature mixture of the two partial flows after flowing through the first heat exchanger is provided.
“Thermally insulated” should be understood in particular to mean that the second flow duct is largely decoupled.
The at least one heat exchanger for charge-air cooling has at least one first flow duct, in particular a plurality of first flow ducts, for a throughflow of a first medium to be cooled, in particular charge air. In addition, the at least one first heat exchanger for charge-air cooling has at least one second flow duct, in particular a plurality of second flow ducts, for a throughflow of first medium which is substantially not to be cooled, in particular charge air, with at least one second flow duct, in particular the plurality of second flow ducts, serving here for bypassing first medium, in particular charge air. In addition, the at least one first heat exchanger has at least one or two third flow ducts, in particular a plurality of third flow ducts, for a throughflow of a coolant and/or refrigerant, in particular of a coolant circuit or of a refrigerant circuit. At least one housing, in particular at least one intake pipe region, serves for holding the at least one first heat exchanger. At least one regulating device for temperature regulation and/or uniform temperature mixture of the first medium, in particular of the charge air, after flowing through the first heat exchanger serves in particular to produce a uniform temperature of the first medium, in particular of the charge air, in that in particular first cooled medium is mixed with first uncooled medium.
In one advantageous embodiment, the regulating device has at least one closure element for closing off the at least one first flow duct and/or the at least one second flow duct at least in regions. The temperature of the first medium, in particular of the charge air and/or of the recirculated exhaust gas, after flowing through the at least first heat exchanger can particularly advantageously be set and regulated in this way.
In one advantageous refinement, the regulating device is designed in the manner of a lamella slide. “In the manner of a lamella slide” is to be understood here in particular to mean that the regulating device is embodied in particular as a slide element which has at least one or a plurality of lamellae. The temperature of the first medium, in particular of the charge air and/or of the recirculated exhaust gas, can particularly advantageously be set, and uncooled first medium particularly advantageously mixed with cooled first medium, in this way.
It can additionally be provided that the at least one closure element is designed in the manner of a lamella and/or has a closure element width which corresponds to a spacing between two adjacently arranged third flow ducts. “In the manner of a lamella” means that the closure element has at least one lamella, in particular a plurality of lamellae. The closure element, in particular the at least one lamella, has a closure element width which corresponds to the spacing between two adjacently arranged third flow ducts. The at least one first flow duct and/or the at least one second flow duct can be particularly advantageously closed off at least in regions in this way.
It can additionally be provided that adjacent closure elements are arranged with that spacing, in particular the spacing between two adjacently arranged third flow ducts, to one another and/or are connected to one another by means of at least one closure connecting element.
In a further advantageous embodiment, the regulating device is arranged at the inflow side or at the outflow side of the at least one first heat exchanger and/or is integrated in the at least one first heat exchanger.
It can additionally be provided that the third flow ducts are designed in the manner of flat tubes and/or in the manner of disks or plates. “In the manner of flat tubes” means in particular that the flow ducts have a slot-shaped cross-sectional area, and/or can be formed from a plurality of individual ducts, which are arranged parallel, with a round and/or rectangular cross section.
In addition, it can particularly preferably be provided that the at least one first flow duct and/or the at least one second flow duct are arranged between adjacent third flow ducts and/or substantially perpendicular to the third flow ducts. In this way, a first medium which flows through the first flow ducts is particularly advantageously cooled, and/or first medium which flows through the second flow ducts is particularly advantageously not cooled.
In a further advantageous embodiment, first flow ducts and second flow ducts are arranged alternately between adjacent third flow ducts, in particular tubes. As a result of the alternating arrangement of a first flow duct, followed by a third flow duct, followed in turn by a second flow duct, followed in turn by a third flow duct etc., a mixture between first uncooled and first cooled medium, in particular charge air and/or exhaust gas, can particularly advantageously take place.
In a further advantageous embodiment, at least one fin element, in particular at least one corrugated fin for increasing cooling power, is arranged in the at least one first flow duct, and/or is connected to at least one third flow duct. In particular first medium which flows in particular through the at least one first flow duct can particularly advantageously be cooled in this way. As a result of at least one fin element being connected to the third flow duct, in particular by means of soldering, welding, adhesive bonding etc., the heat can particularly advantageously be transmitted from the at least one first flow duct via the fins to the third flow ducts, in particular the tubes.
In addition, it can particularly preferably be provided that the housing is embodied as an intake pipe for an engine unit of an internal combustion engine. In this way, the device can be integrated in a particularly optimum manner in terms of installation space into the intake pipe, and heating of the first medium, in particular of the charge air and/or of the recirculated and cooled exhaust gas, can particularly advantageously be prevented.
It can additionally be provided that the at least one first heat exchanger is an evaporator for a refrigerant circuit. In this way, it is possible in particular for the existing refrigerant circuit of an air-conditioning system to particularly advantageously be utilized for cooling the charge air by means of the at least one first heat exchanger.
In one advantageous refinement, at least one throttle flap is arranged at the inflow side and/or outflow side of the at least one first heat exchanger.
It can additionally be provided that an infeed device for feeding recirculated and/or cooled exhaust gas of an internal combustion engine into the first medium is arranged at the inflow side and/or outflow side of the at least one first heat exchanger. In this way, recirculated and/or cooled exhaust gas can particularly advantageously be supplied to the charge air and/or to the internal combustion engine.
In a further advantageous embodiment, the infeed device is designed in the manner of a flat tube and/or has at least one infeed opening for feeding in in particular recirculated and/or cooled exhaust gas. In this way, recirculated and/or cooled exhaust gas can particularly advantageously be fed into the first medium, in particular the charge air, or particularly advantageously mixed with the charge air.
In this way, recirculated and/or cooled exhaust gas can particularly advantageously be supplied both to cooled first medium, in particular charge air, and also to uncooled first medium, in particular charge air, and particularly advantageously mixed therewith.
It can additionally be particularly preferably provided that a mixing device for mixing cooled first medium with uncooled first medium, and/or with in particular recirculated and/or cooled exhaust gas, is arranged at the outflow side of the at least one first heat exchanger and/or of the at least one infeed device. In this way, temperature stranding between uncooled first medium on the one hand and/or substance stranding, in particular of charge air and/or recirculated exhaust gas, on the other hand and cooled first medium can be particularly advantageously prevented or suppressed.
Also proposed is a system having a device for charge-air cooling for an internal combustion engine of a motor vehicle as claimed in one of claims 1 to 17, which system has at least one internal combustion engine, at least one refrigerant circuit with at least one second heat exchanger, in particular with an evaporator for an air-conditioning system, at least one third heat exchanger for charge-air pre-cooling, at least one turbocharger for charging the charge air, at least one fourth heat exchanger, in particular a condenser for an air-conditioning system, and at least one valve device, in particular an expansion valve.
It can additionally be provided that the system has at least one coolant circuit for indirect charge-air cooling, with the coolant circuit having the third heat exchanger for charge-air pre-cooling and at least one fifth heat exchanger for cooling the coolant by means of ambient air.
In a further advantageous embodiment, the system has at least one sixth heat exchanger for exhaust-gas cooling of recirculated exhaust gas for the infeed device. In this way, recirculated and cooled exhaust gas can particularly advantageously be supplied by means of the infeed device to the first medium, in particular the charge air.
Further advantageous embodiments of the invention can be gathered from the subclaims and from the drawing.
The subject matter of the subclaims relate both to the device for charge-air cooling for an internal combustion engine of a motor vehicle according to the invention, and also to the system according to the invention.
Exemplary embodiments of the invention are illustrated in the drawing and are explained in more detail below, the invention not being restricted to these. In the drawing:
FIG. 1 shows a section illustration through a charge-air cooler which is integrated into the intake pipe and has a regulating device which is designed in the manner of a lamella slide,
FIG. 2 shows a front view of a regulating device which is designed in the manner of a lamella slide,
FIG. 3 shows a section illustration A-A through a charge-air cooler having a regulating device which is designed in the manner of a lamella slide,
FIG. 4 shows a first exemplary embodiment of a system for charge-air cooling, and
FIG. 5 shows a second exemplary embodiment of a system for charge-air cooling.
FIG. 1 shows a section illustration through a charge-air cooler 9 which is integrated into the intake pipe 2 and has a regulating device 4 which is designed in the manner of a lamella slide.
The device 1 for charge-air cooling has a housing 2, in particular an intake pipe, in which is arranged at least one first heat exchanger 9, in particular an evaporator. The evaporator has a number of third flow ducts which are embodied as tubes 6. In the illustrated exemplary embodiment, the tubes 6 are embodied as flat tubes. Said flat tubes have a substantially slot-shaped cross section. In another exemplary embodiment (not illustrated), the webs are divided into a plurality of individual ducts.
In another exemplary embodiment, the tubes 6 have a round, elliptical, star-shaped, triangular, rectangular or polygonal cross section, or a cross section with a combination of the above-specified shapes. In the illustrated exemplary embodiment, the tubes 6 are formed from a metal, in particular from aluminum or from noble steel. In another exemplary embodiment, the tubes 6 are formed from a thermally conductive material and/or from ceramic and/or from plastic and/or from a fiber composite material. In the illustrated exemplary embodiment, the first heat exchanger 9 is embodied as an evaporator. In another exemplary embodiment, the first heat exchanger 9 can be embodied as an evaporator of a refrigerant circuit for an air-conditioning system and/or as a condenser of an air-conditioning system and/or as an oil cooler and/or as a transmission oil cooler and/or as a steering oil cooler and/or as an exhaust-gas cooler and/or as a charge-air cooler and/or as a coolant cooler and/or as a gas cooler for an air-conditioning system which is operated in particular with CO₂.
The first heat exchanger 9, in particular the evaporator, has at least one collecting tank. In the illustrated exemplary embodiment, the first heat exchanger 9 has two collecting tanks into which the tubes 6 are inserted and to which the tubes 6 are connected, in particular by means of soldering, welding, adhesive bonding and the like. The collecting tanks (not illustrated) are formed for example from plastic or from a metal such as for example aluminum or steel or noble steel. In addition, the collecting tanks can also be formed from a fiber composite material or from ceramic. In the collecting tanks (not illustrated), the refrigerant and/or the coolant which flows through the tubes 6 is collected and distributed to the tubes 6.
In the illustrated exemplary embodiment, the first heat exchanger 9 has nine tubes 6, in particular flat tubes. In another exemplary embodiment, the heat exchanger 9 has one to nine or more than nine tubes 6, in particular flat tubes.
First flow ducts 7 or second flow ducts 8 are arranged between the tubes 6, in particular the flat tubes, in particular between two adjacent tubes 6. In the illustrated exemplary embodiment, a first flow duct 7, followed by a second flow duct 8 between the next tube pair of tubes 6, are arranged alternately between the tubes 6. The sequence can however also be reversed, so that a second flow duct 8 follows a first flow duct 7 or vice versa.
In another exemplary embodiment, one or two or three or four or five or six etc. first flow ducts 7 can be arranged in series, and followed by one or two or three or four or five or six etc. second flow ducts 8, or vice versa. The first and/or second flow ducts are in each case spaced apart from one another by one or more tubes 6.
As viewed in the air inflow direction LE, the still uncooled or the already pre-cooled charge air initially flows past a throttle flap 3. The throttle flap 3 serves for throttling the charge-air flow. The throttle flap 3 can be adjusted in a continuously variable fashion and has a throttle flap angle α with respect to the air inflow direction LE. The throttle flap angle α can assume values between 0° and 360°. If the throttle flap assumes an angle α=0° or α=180°, then the resistance for the inflowing air is at its lowest. If the throttle flap 3 assumes an angle α=90° or an angle α=270°, then the resistance for the inflowing air is at its greatest. A throttle flap 3 is necessary in the case in particular of spark-ignition engines. In the case of diesel engines, a throttle flap 3 is not strictly necessary. In another exemplary embodiment, the throttle flap can also be arranged, as viewed in the air flow direction LE, downstream of the regulating device 4 and/or downstream of the first heat exchanger 9 and/or downstream of the infeed device 10 and/or downstream of the mixing device 12. In another exemplary embodiment, more than one throttle flap 3 is arranged in the device 1.
A regulating device 4 is arranged upstream of the first heat exchanger, in particular the evaporator, as viewed in the air flow direction LE. In the illustrated exemplary embodiment, the regulating device 4 is designed as a lamella slide 4. The regulating device, in particular the lamella slide, has a plurality of closure elements 5. The closure elements 5 are embodied for example as lamellae. The lamellae have a substantially rectangular shape. In another exemplary embodiment, the closure elements, in particular the lamellae, may have a round and/or elliptical and/or triangular and/or rectangular and/or polygonal shape or a shape resulting from the combination of the above-specified shapes. In the illustrated exemplary embodiment, the regulating device, in particular the lamella slide, assumes a position in which the second flow ducts 8 are closed off, so that first medium, in particular charge air, can flow only through the first flow ducts 7 and thereby be cooled. In a further position which is not illustrated in the illustrated exemplary embodiment in FIG. 1, the closure elements 5 close off only the first flow ducts 7, so that first medium, in particular charge air, flows only through the second flow ducts 8 and is thereby substantially cooled to a negligible degree. In addition, the regulating device can, in another, likewise not illustrated position, close off the first flow ducts 7 and the second flow ducts 8 at least in sections, so that first medium, in particular charge air, flows both through the first flow ducts 7 and also through the second flow ducts 8, with the proportion of the first medium which flows through the first flow ducts 7 being cooled, and the proportion of the first medium which flows through the second flow ducts 8 substantially not being cooled.
In another exemplary embodiment, the regulating device, in particular the lamella slide, is arranged downstream of the first heat exchanger 9, in particular downstream of the evaporator, as viewed in the air inflow direction LE. In another exemplary embodiment, the regulating device 4, in particular the lamella slide, is arranged in the first heat exchanger 9, in particular in the evaporator, or is formed in one piece therewith or is integrated into the first heat exchanger 9, in particular the evaporator. Arranged adjacent to the first heat exchanger 9, in particular the evaporator, is an expansion valve 17. The expansion valve 17 is connected to a refrigerant circuit (not illustrated in any more detail). From the expansion valve 17, a refrigerant inlet line 18 leads into a collecting tank (not illustrated) of the first heat exchanger, of the evaporator, 9. A refrigerant outlet line 19 leads from a collecting tank (not illustrated) of the first heat exchanger 9 to the expansion valve 17. The expansion valve 17 can be embodied as a thermostatic expansion valve and/or as an orifice. The refrigerant arrives at increased pressure upstream of the expansion valve 17. In the expansion valve 17, the pressure of the refrigerant, in particular R734a or CO₂, or the pressure of another refrigerant, is reduced, and the refrigerant flows with the lower pressure into the first heat exchanger 9, in particular the evaporator. During the expansion of the refrigerant after flowing through the expansion valve 17, the temperature of the refrigerant is reduced on account of the lower pressure and of the relationship between pressure and temperature.
As viewed in the air inflow direction LE, an infeed device 10 is arranged downstream of the first heat exchanger 9. In the infeed device 10, recirculated exhaust gas and/or recirculated exhaust gas which is cooled in the exhaust-gas heat exchanger 16 is supplied via infeed openings 11 in infeed tubes, recirculated and/or cooled exhaust gas is supplied to the first medium, in particular the charge air. In the illustrated exemplary embodiment, the infeed device 10 has nine infeed openings 11 and/or infeed tubes. In another exemplary embodiment, the infeed device 10 has one to nine or more than nine infeed openings 11 and/or infeed tubes.
In another exemplary embodiment, the infeed device 10 is arranged upstream of the first heat exchanger 9 as viewed in the air inflow direction LE or in the first heat exchanger 9. In another exemplary embodiment, the infeed device 10 is formed in one piece with or is integrated into the first heat exchanger 9, in particular the evaporator.
The first heat exchanger 9, in particular the evaporator, is preferably embodied as a segmented evaporator. In the illustrated exemplary embodiment, the exhaust-gas heat exchanger is formed as a low-temperature exhaust-gas heat exchanger. In another exemplary embodiment, the exhaust-gas heat exchanger can be embodied as a direct exhaust-gas cooler. In a further exemplary embodiment, the exhaust-gas cooler can be embodied as an indirect exhaust-gas cooler. The at least one exhaust-gas cooler 16 can be arranged on the low-pressure side of a turbine (not illustrated) of at least one turbocharger. In another exemplary embodiment, the exhaust-gas heat exchanger 16 can be arranged on the high-pressure side of a turbine of a turbocharger (not illustrated).
In the illustrated exemplary embodiment, a mixing device 12 is arranged downstream of the infeed device 10 as viewed in the air inflow direction LE. In the illustrated exemplary embodiment, the mixing device 12 is embodied as a static mixer. The mixing device 12 is embodied substantially as a grate which mix uncooled first medium, charge air, and/or cooled first medium, charge air, and/or supplied cooled exhaust gas with one another. In the illustrated exemplary embodiment, the static mixer is formed from a metal wire, in particular from aluminum, steel or noble steel or from plastic or from a ceramic material and/or from a fiber composite material. The mixing device 12 has turbulence-generating elements (not illustrated in any more detail) such as for example wire grates or embossings. The mixing device 12 is produced in particular of a primary shaping production method such as for example casting, in particular injection molding, or by means of a material-removal production method such as for example lasing or eroding, or by means of a shaping production method such as for example by means of stamping, embossing or punching. In another exemplary embodiment, the mixing device 12 is arranged upstream of the infeed device 10 as viewed in the flow direction LE. In another exemplary embodiment, the mixing device 12 is formed in one piece with the first heat exchanger 9, in particular the evaporator, and/or in one piece with the infeed device 10 and/or in one piece with the regulating device 4.
After flowing through the mixing device 12, the cooled charge air and/or the charge air which is provided with recirculated cooled exhaust gas is split up in the air distribution chamber 15 to the air supply ducts 14 which lead to the engine 13. In the illustrated exemplary embodiment, the engine 13 has four air supply ducts 14. In another exemplary embodiment, the engine 13 has one to four or five, six, seven, eight or more than eight air supply ducts 14.
In the illustrated exemplary embodiment, the infeed device 10 is embodied substantially as a flat tube. In another exemplary embodiment, the infeed device 10 has a round and/or elliptical and/or triangular and/or rectangular shape and/or a combination of the above-specified shapes. In the illustrated exemplary embodiment, the infeed device 10 is formed from metal, in particular from aluminum or from noble steel. In another exemplary embodiment, the infeed device 10 is formed from plastic and/or from ceramic and/or from a fiber composite material.
In another exemplary embodiment which is not illustrated, the mixing device 12 can likewise have a filter unit.
In the illustrated exemplary embodiment, the regulating device 4 and/or the infeed device 10 and/or the mixing device 12 are arranged substantially perpendicular to the air inflow device LE. In another exemplary embodiment, the regulating device 4 and/or the infeed device 11 and/or the mixing device 12 enclose an angle (not illustrated) of 0° to 360°, in particular between 0° and 270°, in particular between 0° and 180°, in particular between 0° and 100°, in particular between 20° and 95°, in particular between 30° and 90°.
In the illustrated exemplary embodiment, the housing 2, in particular the intake pipe, is formed from metal, in particular from noble steel, steel or heat-resistant aluminum or from a heat-resistant plastic or from ceramic or from a fiber composite material.
FIG. 2 shows a front view of a regulating device 4 which is designed in the manner of a lamella slide, and the device for charge-air cooling 1 and the first heat exchanger 9. Identical features are provided with the same reference symbols as in FIG. 1.
FIG. 2 illustrates a detail of the device 1 for charge-air cooling. The device 1 for charge-air cooling comprises a first heat exchanger 9, in particular an evaporator, having 2 collecting tanks 20. Seven tubes 6, in particular flat tubes, connect the two collecting tanks 20. The tubes 6, in particular the flat tubes, are connected to the collecting tanks by means of cohesive joining, in particular by means of soldering, welding, adhesive bonding etc. and/or by means of a form-fitting connection, in particular by means of crimping or bending, to the collecting tanks 20. A refrigerant, in particular R134a or CO₂or another refrigerant, flows in the tubes 6. In the illustrated exemplary embodiment, the regulating device 4, in particular the lamella slide, with its closure elements 5, in particular with its lamellae, closes off the first flow ducts 7. The second flow ducts 8 are opened.
The closure elements 5, in particular the lamellae, are connected to one another by means of closure connecting elements 21. In another exemplary embodiment, the closure elements 5 and the closure connecting elements 21 are formed in one piece. Adjacent closure elements 5, in particular lamellae, have a spacing b2 to one another. The spacing b2 can assume values between 0 mm and 20 mm, in particular between 0 mm and 15 mm, in particular between 0 mm and 12 mm, in particular between 2 mm and 10 mm, in particular between 5 mm and 8 mm. In the illustrated exemplary embodiment, the closure connecting elements 21 are formed substantially parallel to the collecting tanks 20. In another exemplary embodiment, the closure connecting elements 21 are formed at an angle of between 0° and 360°, in particular between 0° and 180°, in particular between 5° and 100°, in particular between 5° and 90°, in particular between 5° and 70°, with respect to one another.
In the illustrated exemplary embodiment, the closure elements 5, in particular the lamellae, are arranged substantially perpendicular to the closure connecting elements 21 and/or to the collecting tanks 20. In another exemplary embodiment, the closure elements 5, in particular the lamellae, are formed at an angle (not illustrated) between 0° and 90°, in particular between 0° and 80°, in particular between 0° and 70°, with respect to the closure connecting elements 21 and/or to the collecting tanks 20.
The tubes 6 are arranged substantially perpendicular to the collecting tanks 20.
The closure elements 5, in particular the lamellae, are in particular of strip-shaped form. Each lamella 5 is so wide that it completely covers the first flow duct 7 or the second flow duct 8. All the closure elements 5, in particular all the lamellae, are movable transversely with respect to the first heat exchanger, in particular with respect to the evaporator, by at least the width b2+d or by the width b1+d or by the width a+d.
FIG. 3 shows a section illustration A-A through the device 1 or through the charge-air cooler 9 and the regulating device 4 which is designed in the manner of a lamella slide. Identical features are provided with the same reference symbols as in the preceding figures.
The device 1 in FIG. 3 shows the first heat exchanger 9, in particular the evaporator with the tubes 6, in particular the flat tubes. In addition, the infeed device 10 for feeding in recirculated and/or cooled exhaust gas AGR is arranged on the first heat exchanger 9. The infeed device 10 has infeed openings 11. The infeed openings 11 are of substantially slot-shaped design and have a slot width sb. The slot width sb assumes values between 0 mm and 20 mm, in particular values between 0 mm and 15 mm, in particular values between 1 mm and 10 mm, in particular values between 1 mm and 8 mm.
Fin elements 22 are arranged alternately between the flat tubes 6. The fin elements 22 are in particular arranged in the first flow ducts 7. In another exemplary embodiment (not illustrated), the fin elements 22 are arranged in the second flow ducts 8. The fin elements 22 are connected to the flat tubes 6 in a cohesively joined manner, for example by means of soldering, welding, adhesive bonding etc. The fin elements 22 are formed from metal, in particular from aluminum. The fin elements 22 have a number of slots (not illustrated). The fin elements 22 are in particular formed as corrugated fins. The tubes 6, in particular the flat tubes, have a depth t. The depth t assumes values from 10 mm to 200 mm, in particular values between 10 mm and 100 mm, in particular values between 10 mm and 60 mm, in particular values between 20 mm and 60 mm.
The flat tubes 6 have a thickness d. The thickness d assumes values between 0 mm and 5 mm, in particular values between 0 mm and 4 mm, in particular values between 0.1 mm and 3 mm, in particular values between 0.1 mm and 2.8 mm.
The infeed openings 11 are arranged substantially perpendicular to the tubes 6. The infeed openings 11 are substantially arranged such that, with the elongation of the flat tubes 6 in the direction of the depth t, the infeed opening is divided into two parts which have substantially the same surface area.
Adjacent flat tubes have a spacing a to one another. The spacing a assumes values between 0 mm and 15 mm, in particular values between 5 mm and 15 mm, in particular values between 5 mm and 12 mm, in particular values between 5 mm and 10 mm, in particular values between 5 mm and 8 mm. In the illustrated exemplary embodiment, the width of the first flow duct b1 and/or the width of the second flow duct b2 assumes the same values as the spacing a between two adjacent tubes 6. In another exemplary embodiment, the spacing a is smaller than the width b1 and/or the width b2. In another exemplary embodiment, the spacing a is greater than the width of the first flow duct b1 and/or than the width of the second flow duct b2.
In another exemplary embodiment, the width of the first flow duct b1 can be greater than or less than or equal to the width of the second flow duct b2.
FIG. 4 shows a first exemplary embodiment of a system for charge-air cooling. The same features are provided with the same reference symbols as in the preceding figures.
The system 40 for charge-air cooling has a fan and a condenser and a coolant cooler. The fan L conveys ambient air through the condenser KO and/or through the coolant cooler KMK. In the illustrated exemplary embodiment, the fan is arranged upstream of the condenser KO and upstream of the coolant cooler KMK in the air flow direction. In another exemplary embodiment, the fan L is arranged downstream of the condenser KO and/or downstream of the coolant cooler KMK. In addition, the system 40 has a coolant pump P, a first compressor K1 for compressing a refrigerant, in particular CO₂or R134a. In addition, the system 40 has at least one turbocharger TL, a charge-air pre-cooler LLVK and a device for charge-air cooling 9 having a first heat exchanger 9, in particular an evaporator. The system 40 additionally has an internal combustion engine 13 and an expansion valve 17, a refrigerant evaporator of an air-conditioning system KV and a further expansion valve V1.
Air which is sucked in from the outside is compressed in the turbocharger TL or, in a further embodiment (not illustrated) of a further second compression, is further compressed after already the first passage through a compression stage. This leads to an increase of the temperature of the charge air, as a result of which the charge air is cooled in a charge-air pre-cooler LLVK in a first stage and is cooled further in the device for charge-air cooling 1, in particular in the first heat exchanger 9, in particular the evaporator, before the charge air is supplied to the internal combustion engine 13.
The charge-air pre-cooler LLVK is traversed by a coolant, in particular a water-containing coolant. After flowing through the charge-air pre-cooler LLVK, the coolant flows through the coolant cooler KMK and further through the coolant pump P and back to the charge-air pre-cooler LLVK. The pump P can also be arranged between the charge-air pre-cooler LLVK and the coolant cooler KMK. The coolant circuit KÜK has the coolant cooler KMK, the charge-air pre-cooler LLVK and the coolant pump P.
In the refrigerant circuit KÄK, refrigerant, in particular CO₂or R134a, is brought to a higher pressure level in a refrigerant compressor K1 and flows through the condenser KO, with the refrigerant being cooled by the ambient air. After flowing through the condenser, the refrigerant flows further through the refrigeration circuit KÄK, with a refrigerant circuit bypass KÄKB branching off from the refrigerant circuit KÄK. Through the refrigerant bypass, refrigerant flows through an expansion valve 17 into the first heat exchanger 9, in particular the evaporator, of the device 1 for charge-air cooling, and subsequently flows back into the refrigerant circuit KÄK. The remaining part of the refrigerant flows via a further expansion valve V1, with the pressure of the refrigerant being reduced, into the evaporator of an air-conditioning system of a motor vehicle.
FIG. 5 shows a second exemplary embodiment of a system for charge-air cooling. The same features are provided with the same reference symbols as in the preceding figures.
The system 50 for charge-air cooling, in contrast to the system which is illustrated in FIG. 4, has a further valve V2. The valve V2 is embodied in particular as a bypass valve and regulates the flow through the refrigerant circuit bypass KÄKB and/or through the refrigerant circuit KÄK. In particular, the valve V2 permits a flow exclusively through the refrigerant circuit bypass KÄKB and/or through the refrigerant circuit KÄK. The coolant circuit KÜK is not illustrated in the system 50. In another exemplary embodiment, the charge-air pre-cooler LLVK is a direct charge-air cooler which is cooled and/or acted on directly by ambient air.
The features of the various exemplary embodiments can be combined with one another in any desired way. The invention can also be used in fields other than those shown.
This application claims priority from German Patent Application No. 10 2006 048 485.1, filed Oct. 11, 2006, all of which is incorporated herein by reference in its entirety.

Claims

1. A device for charge-air cooling for an internal combustion engine of a motor vehicle, having

at least one first heat exchanger for charge-air cooling with at least one first flow duct for a throughflow of a first partial flow of a first medium, with at least one second flow duct for a throughflow of a second partial flow of the first medium, and with at least one third flow duct for a throughflow of a coolant and/or refrigerant, with the first flow duct being thermally connected to the at least one third flow duct, and the at least one second flow duct being thermally insulated, wherein

at least one regulating device for temperature regulation and uniform temperature mixture of the two partial flows after flowing through the first heat exchanger is provided.

2. The device as claimed in claim 1, wherein the regulating device has at least one closure element for closing off the at least one first flow duct and/or the at least one second flow duct at least in regions.

3. The device as claimed in claim 1, wherein the regulating device is designed in the manner of a lamella slide.

4. The device as claimed in claim 2, wherein the at least one closure element is designed in the manner of a lamella and/or has a closure element width which corresponds to a first spacing between two adjacently arranged third flow ducts.

5. The device as claimed in claim 2, wherein adjacent closure elements are arranged with a second spacing to one another and/or are connected to one another by means of at least one closure connecting element.

6. The device as claimed in claim 1, wherein the regulating device is arranged at the inflow side or at the outflow side of the at least one first heat exchanger and/or is integrated in the at least one first heat exchanger.

7. The device as claimed in claim 1, wherein the at least one flow duct is designed in the manner of a flat tube and/or in the manner of a disk or plate.

8. The device as claimed in claim 1, wherein the at least one first flow duct and/or the at least one second flow duct are arranged between adjacent third flow ducts and/or substantially perpendicular to the third flow ducts.

9. The device as claimed in claim 1, wherein first flow ducts and second flow ducts are arranged alternately between adjacent third flow ducts.

10. The device as claimed in claim 1, wherein at least one fin element, in particular at least one corrugated fin for increasing heat transfer, is arranged in the at least one first flow duct, and/or is connected to at least one third flow duct.

11. The device as claimed in claim 1, wherein at least one housing for holding the at least one first heat exchanger is embodied as an intake pipe for an engine unit.

12. The device as claimed in claim 1, wherein the at least one first heat exchanger is an evaporator for a refrigerant circuit.

13. The device as claimed in claim 1, wherein at least one additional throttle flap is arranged at the inflow side and/or outflow side of the at least one first heat exchanger.

14. The device as claimed in claim 1, wherein an infeed device for feeding recirculated and/or cooled exhaust gas of an internal combustion engine into the first medium is arranged at the inflow side and/or outflow side of the at least one first heat exchanger.

15. The device as claimed in claim 14, wherein the infeed device is designed in the manner of a flat tube and/or has at least one infeed opening for feeding in in particular recirculated and/or cooled exhaust gas.

16. The device as claimed in claim 15, wherein the at least one infeed opening is designed substantially in the manner of a slot and/or is arranged substantially perpendicular to a charge-air flow direction.

17. The device as claimed in claim 1, wherein a mixing device for mixing cooled first medium with uncooled first medium, and/or with in particular recirculated and/or cooled exhaust gas, is arranged at the outflow side of the at least one first heat exchanger and/or of the at least one infeed device.

18. A system having a device as claimed in claim 1, having

at least one internal combustion engine,

at least one refrigerant circuit with at least one second heat exchanger, in particular with an evaporator for an air-conditioning system,

at least one third heat exchanger for charge-air pre-cooling, and at least one turbocharger for charging the charge air.

19. The system as claimed in claim 18, wherein the system has at least one fourth heat exchanger, in particular a condenser for an air-conditioning system, and/or at least one valve device, in particular an expansion valve.

20. The system as claimed in claim 18, wherein the system has at least one coolant circuit for indirect charge-air cooling, with the third heat exchanger for charge-air pre-cooling being arranged in the coolant circuit, and/or the system having at least one fifth heat exchanger for cooling the coolant by means of ambient air.

21. The system as claimed in claim 18, wherein the system has at least one sixth heat exchanger for exhaust-gas cooling for the infeed device.