U.S. patent application number 11/870172 was filed with the patent office on 2008-04-17 for apparatus for cooling charge air for a combustion engine, system with an apparatus for cooling charge air.
This patent application is currently assigned to BEHR GmbH & Co. KG. Invention is credited to Roland Burk.
Application Number | 20080087402 11/870172 |
Document ID | / |
Family ID | 39092270 |
Filed Date | 2008-04-17 |
United States Patent
Application |
20080087402 |
Kind Code |
A1 |
Burk; Roland |
April 17, 2008 |
Apparatus for cooling charge air for a combustion engine, system
with an apparatus for cooling charge air
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.
Inventors: |
Burk; Roland; (Stuttgart,
DE) |
Correspondence
Address: |
FOLEY AND LARDNER LLP;SUITE 500
3000 K STREET NW
WASHINGTON
DC
20007
US
|
Assignee: |
BEHR GmbH & Co. KG
|
Family ID: |
39092270 |
Appl. No.: |
11/870172 |
Filed: |
October 10, 2007 |
Current U.S.
Class: |
165/101 |
Current CPC
Class: |
Y02T 10/146 20130101;
F02M 35/10222 20130101; Y02T 10/12 20130101; F02M 26/19 20160201;
F02M 35/10268 20130101; F02B 29/0475 20130101; F02M 26/11 20160201;
F02M 26/05 20160201; F02B 29/0443 20130101; F02M 26/06 20160201;
F01P 2060/02 20130101; F02M 35/10262 20130101; F02B 29/0493
20130101; F02M 26/30 20160201 |
Class at
Publication: |
165/101 |
International
Class: |
F28F 27/02 20060101
F28F027/02 |
Foreign Application Data
Date |
Code |
Application Number |
Oct 11, 2006 |
DE |
10 2006 048 485.1 |
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.
Description
[0001] 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.
[0002] 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.
[0003] 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.
[0004] 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.
[0005] A device for cooling charge air is also known from
EP1342893.
[0006] 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.
[0007] Said object is achieved by means of the features of claim
1.
[0008] 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.
[0009] "Thermally insulated" should be understood in particular to
mean that the second flow duct is largely decoupled.
[0010] 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.
[0011] 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.
[0012] 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.
[0013] 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.
[0014] 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.
[0015] 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.
[0016] 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.
[0017] 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.
[0018] 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.
[0019] 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.
[0020] 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.
[0021] 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.
[0022] 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.
[0023] 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.
[0024] 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.
[0025] 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.
[0026] 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.
[0027] 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.
[0028] 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.
[0029] 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.
[0030] Further advantageous embodiments of the invention can be
gathered from the subclaims and from the drawing.
[0031] 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.
[0032] 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:
[0033] 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,
[0034] FIG. 2 shows a front view of a regulating device which is
designed in the manner of a lamella slide,
[0035] 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,
[0036] FIG. 4 shows a first exemplary embodiment of a system for
charge-air cooling, and
[0037] FIG. 5 shows a second exemplary embodiment of a system for
charge-air cooling.
[0038] 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.
[0039] 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.
[0040] 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
CO.sub.2.
[0041] 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.
[0042] 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.
[0043] 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.
[0044] 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.
[0045] 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 .alpha.
with respect to the air inflow direction LE. The throttle flap
angle .alpha. can assume values between 0.degree. and 360.degree..
If the throttle flap assumes an angle .alpha.=0.degree. or
.alpha.=180.degree., then the resistance for the inflowing air is
at its lowest. If the throttle flap 3 assumes an angle
.alpha.=90.degree. or an angle .alpha.=270.degree., 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.
[0046] 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.
[0047] 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 CO.sub.2, 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.
[0048] 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.
[0049] 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.
[0050] 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).
[0051] 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.
[0052] 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.
[0053] 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.
[0054] In another exemplary embodiment which is not illustrated,
the mixing device 12 can likewise have a filter unit.
[0055] 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.degree. to 360.degree., in particular
between 0.degree. and 270.degree., in particular between 0.degree.
and 180.degree., in particular between 0.degree. and 100.degree.,
in particular between 20.degree. and 95.degree., in particular
between 30.degree. and 90.degree..
[0056] 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.
[0057] 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.
[0058] 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 CO.sub.2 or 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.
[0059] 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.degree. and 360.degree., in particular between 0.degree. and
180.degree., in particular between 5.degree. and 100.degree., in
particular between 5.degree. and 90.degree., in particular between
5.degree. and 70.degree., with respect to one another.
[0060] 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.degree. and 90.degree., in particular
between 0.degree. and 80.degree., in particular between 0.degree.
and 70.degree., with respect to the closure connecting elements 21
and/or to the collecting tanks 20.
[0061] The tubes 6 are arranged substantially perpendicular to the
collecting tanks 20.
[0062] 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.
[0063] 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.
[0064] 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.
[0065] 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.
[0066] 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.
[0067] 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.
[0068] 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.
[0069] 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.
[0070] 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.
[0071] 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 CO.sub.2 or 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.
[0072] 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.
[0073] 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 KUK has the coolant cooler KMK, the charge-air
pre-cooler LLVK and the coolant pump P.
[0074] In the refrigerant circuit KAK, refrigerant, in particular
CO.sub.2 or 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 KAK, with a refrigerant circuit bypass KAKB
branching off from the refrigerant circuit KAK. 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 KAK. 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.
[0075] 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.
[0076] 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 KAKB and/or through
the refrigerant circuit KAK. In particular, the valve V2 permits a
flow exclusively through the refrigerant circuit bypass KAKB and/or
through the refrigerant circuit KAK. The coolant circuit KUK 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.
[0077] 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.
[0078] 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.
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