DE102016001650A1 - Cooling device for a motor vehicle, in particular a passenger car - Google Patents

Abstract

The invention relates to a cooling device (10) for a motor vehicle, with a first cooling circuit (12) through which a cooling medium can flow, in which an internal combustion engine (16) for driving the motor vehicle, at least one cooler (30) for cooling the first cooling circuit (12 ) and at least one first pump (32) for conveying the cooling medium through the first cooling circuit (12) are arranged, and with a second cooling circuit (14) through which a cooling medium, in which at least one exhaust gas recirculation cooler (52) and at least one second Pump (56) for conveying the cooling medium through the second cooling circuit (14) are arranged, wherein the cooling circuits (12, 14) fluidly separated from each other, but are connected to each other for heat exchange, wherein the pumps (32, 56) as independently operable, electric pumps (32, 56) are formed.

Description

The invention relates to a cooling device for a motor vehicle, in particular a passenger car, according to the preamble of patent claim 1.

Such a cooling device for a motor vehicle, especially passenger cars, is for example the DE 10 2008 036 277 A1 to be known as known. The cooling device comprises a first cooling circuit through which a cooling medium, in particular a cooling liquid, can flow, in which an internal combustion engine for driving the motor vehicle is arranged. Thus, the cooling medium flowing through the first cooling circuit can flow through the internal combustion engine, so that the internal combustion engine can be cooled as a result of a heat transfer from the internal combustion engine to the cooling medium flowing through the first cooling circuit. In the first cooling circuit, at least one cooler for cooling the cooling medium flowing through the first cooling circuit is furthermore arranged. The cooler is for example a heat exchanger. As a result of the cooling of the internal combustion engine, the cooling medium flowing through the first cooling circuit is heated, with the cooling medium, which is heated thereby, flowing through the first cooling circuit, being able to be cooled again by means of the cooler. In addition, at least one first pump for conveying the cooling medium through the first cooling circuit is arranged in the first cooling circuit.

The cooling device further comprises a second cooling circuit, through which a cooling medium can flow, in which at least one exhaust gas recirculation cooler is arranged. The exhaust gas recirculation cooler is for example part of an exhaust gas recirculation device. The exhaust gas recirculation device comprises at least one exhaust gas recirculation line, by means of which exhaust gas of the internal combustion engine is traceable to an intake tract of the internal combustion engine and introduced into the intake tract. In this case, the exhaust gas recirculation cooler is arranged in the exhaust gas recirculation line, so that the exhaust gas flowing through the exhaust gas recirculation line can be cooled by means of the exhaust gas recirculation cooler. The exhaust gas recirculation cooler can thus be flowed through by the exhaust gas and by the cooling medium flowing through the second cooling circuit, so that, for example, a heat transfer from the exhaust gas to the cooling medium flowing through the exhaust gas recirculation cooler can take place via the exhaust gas recirculation cooler. As a result, the recirculated exhaust gas is cooled. In addition, at least one second pump for conveying the cooling medium through the second cooling circuit is arranged in the second cooling circuit.

In addition, the disclosed DE 199 60 960 C1 a heat exchange system for the heating of a vehicle with hybrid drive, being used to control an electric motor of the hybrid drive power semiconductors, which emit heat while driving and which are cooled by a flowing in a cooling circuit, the power semiconductors cooling fluid, which can flow through a heating heat exchanger of the vehicle. It is provided that an internal combustion engine of the hybrid drive has a mechanical cooling fluid pump in an engine cooling circuit.

Object of the present invention is to develop a cooling device of the type mentioned in such a way that a particularly advantageous and needs-based cooling is feasible.

This object is achieved by a cooling device having the features of patent claim 1. Advantageous embodiments with expedient developments of the invention are specified in the remaining claims.

In order to develop a cooling device specified in the preamble of claim 1 type such that a particularly advantageous and needs-based cooling is feasible, it is provided according to the invention that the cooling circuits are fluidly separated from each other, but connected to heat exchange, the pumps as independent of each other operated, electric pumps, that is designed as electrically operable pumps. Since the internal combustion engine for driving the motor vehicle is arranged in the first cooling circuit, the first cooling circuit is also referred to as the main cooling circuit. In particular, the main cooling circuit is a high-temperature cooling circuit, so that the cooling medium flowing through the first cooling circuit flows through the first cooling circuit at a first temperature. The second cooling circuit is thus, for example, a secondary cooling circuit, which is designed for example as a low-temperature cooling circuit, wherein the cooling medium flowing through the second cooling circuit flows through the secondary cooling circuit, for example with a second temperature lower than the first temperature. The exhaust gas recirculation cooler (EGR cooler) is integrated in its own cooling circuit in the form of the second cooling circuit, which is fluidically or hydraulically connected to the main cooling circuit for heat exchange, but operated completely independent of the main cooling circuit, in particular regulated or controlled, can be. In other words, the cooling circuits of the cooling device according to the invention are indeed connected to each other for heat exchange, so that the cooling circuits or the cooling media flowing through the cooling circuits heat can exchange, however, the cooling circuits are completely independent of each other fluidly or hydraulically controlled due to the use of electric or electrically operable pumps. Thereby, a pressure drop in the main cooling circuit can be kept particularly low, wherein the main cooling circuit can be adequately supplied by means of the first electric pump. In addition, it is possible through the use of cooling circuits, the internal combustion engine as a base engine and the exhaust gas recirculation cooler independently as needed to cool, which allows at least substantially optimal, low emissions with minimal power requirements for the operation of the respective cooling circuit. The cooling device according to the invention thus contributes to the emission reduction and fuel consumption reduction alike.

Furthermore, it is possible to keep the respective electrical power, in particular rated power, and the respective space requirement of the respective pump particularly low, so that the space requirement and the weight of the cooling device can be kept low overall. The cooling device can be used particularly advantageously for a combustion engine designed as a diesel engine, in particular a highly loaded diesel engine, wherein the cooling device according to the invention enables the economical conversion of electric pumps for diesel engines of a specific high load.

The respective cooling medium is for example a cooling liquid, which is also referred to as cooling water. Therefore, the respective pump is for example also referred to as a water pump. The cooling device according to the invention enables a targeted and flexible cooling of the respective components in the respective cooling circuit with the lowest power consumption and thus solves the conflict between the realization of low emissions by sufficient cooling of zurückzuführendem exhaust gas and the realization of a low energy demand for operation of the respective pump. The first pump is a main pump because it is located in the main cooling circuit. Since the independently operable, in particular controllable or controllable, pumps are used, it is possible, in particular during a warm-up of the internal combustion engine, that the second pump is activated while the first pump is deactivated or can remain deactivated. This makes it possible that by means of the activated second pump, the cooling medium is conveyed through the second cooling circuit, while the first pump is deactivated, so that caused by the first pump conveying the coolant through the first cooling circuit is omitted. As a result, an excessively high, unnecessary energy consumption of the cooling device can be avoided.

Further advantages, features and details of the invention will become apparent from the following description of a preferred embodiment and from the drawing. The features and feature combinations mentioned above in the description as well as the features and feature combinations mentioned below in the figure description and / or alone in the single figure can be used not only in the respectively indicated combination but also in other combinations or alone, without the frame to leave the invention.

The drawing shows in the single FIGURE is a schematic representation of a cooling device for a motor vehicle, especially passenger cars, with two flowed through by a respective coolant cooling circuits, which are fluidly and connected to each other for heat exchange, wherein in the respective cooling circuit, a respective electric pump for conveying the respective cooling medium is arranged.

The single FIGURE shows a schematic representation of a whole 10 designated cooling device for a motor vehicle, in particular a passenger car. The cooling device 10 has a first cooling circuit through which a cooling medium can flow 12 and a second cooling circuit through which a cooling medium can flow 14 on. To the the respective cooling circuits 12 and 14 to be able to differentiate conceptually better from one another by means of cooling media, this becomes the first cooling circuit 12 flowing through the cooling medium as the first cooling medium and the second cooling circuit 14 flowing through cooling medium referred to as the second cooling medium. In this case, however, the first cooling medium can be the second cooling medium or vice versa, so that the cooling media are identical or the same, for example. The respective cooling medium is for example a cooling liquid, which is also referred to as cooling water. Therefore, the respective refrigeration cycle 12 respectively 14 for example, also referred to as a water cycle.

The car includes a whole with 16 designated internal combustion engine, which is designed for example as a reciprocating internal combustion engine. Preferably, the internal combustion engine 16 designed as a diesel engine. The internal combustion engine 16 includes a crankcase 18 in which, for example, an output shaft, not shown in the figure, about an axis of rotation relative to the crankcase 18 is rotatably mounted. About the crankshaft, the internal combustion engine 16 Providing torques for driving the motor vehicle. By the crankcase, for example, several Combustion chambers in the form of cylinders of the internal combustion engine 16 limited.

The internal combustion engine 16 further includes a separate from the crankcase 18 trained and with the crankcase 18 connected cylinder head 20 through which, for example, respective combustion chamber roofs of the cylinders are formed. Here is the internal combustion engine 16 in the first cooling circuit 12 arranged so that the first cooling medium through the internal combustion engine 16 can flow. In this case, the crankcase 18 at least a first cooling jacket, which is also referred to as a water jacket and in the first cooling circuit 12 is arranged, so that the first cooling jacket can be flowed through by the first cooling medium.

The cylinder head 20 has a second, lower cooling jacket 22 and a third, upper cooling jacket 24 on, with the cooling jackets 22 and 24 Also known as water jackets. Also the cooling jackets 22 and 24 are in the first cooling circuit 12 arranged and thus flowed through by the first cooling medium. The internal combustion engine 16 is thus due to a heat transfer from the internal combustion engine 16 can be cooled or cooled to the first cooling medium. As a result of this heat transfer, the first cooling medium is heated.

The internal combustion engine 16 includes a distribution bar 26 which are also in the first cooling circuit 12 is arranged. By means of the distribution bar 26 the first cooling medium is applied to the first cooling jacket (not shown in detail in FIG. 1), the second cooling jacket 22 and the third cooling jacket 24 distributed. For example, from the first cooling jacket, the second cooling jacket 22 and the third cooling jacket 24 For example, the first cooling medium may become one in the first cooling circuit 12 arranged collecting bar 28 flow, leaving the first coolant the collection bar 28 can flow through. By means of the collection bar 28 the first cooling medium is conducted in the manner explained below.

In the first cooling circuit 12 is at least a cooler 30 arranged, by means of which the first cooling medium can be cooled. As the internal combustion engine 16 in the first cooling circuit 12 is arranged, the first cooling circuit 12 also referred to as the main cooling circuit. Thus, the radiator 30 referred to as the main cooler. The cooler 30 is designed for example as a heat exchanger, so that the cooler 30 flowing through the first cooling medium, for example due to a heat transfer from the first cooling medium via the radiator 30 to the radiator 30 around flowing air can be cooled.

In the first cooling circuit 12 is at least a first pump 32 arranged, by means of which the first cooling medium through the first cooling circuit 12 can be promoted. Since the first cooling medium is formed for example as a cooling liquid, which is also referred to as cooling water, the first pump 32 Also referred to as a water pump or first water pump. From the Fig. It can be seen that the first cooling medium by means of the pump 32 - if this is activated - to the distribution bar 26 is promoted, so that the first cooling circuit 12 closed is.

Furthermore, in the first cooling circuit 12 a thermostat 34 arranged. By means of the collection bar 28 the first cooling medium becomes a thermostat 34 guided, by means of which the first cooling medium on the radiator 32 and on a the radiator 32 immediate bypass 36 is divided. In other words, by means of the thermostat 34 a the cooler 30 flowing through first amount of the first cooling medium and a bypass line 36 flowing through the second amount of the first cooling medium adjustable. That the radiator 30 flowing through first cooling medium is by means of the radiator 30 cooled. The bypass line 36 flowing cooling medium bypasses the radiator 30 , By this is meant that the bypass line 36 flowing cooling medium not through the radiator 30 but directly to the pump 32 flows, so that's the bypass line 36 flowing through cooling medium not by means of the cooler 30 is cooled. After flowing through the radiator 30 can the first cooling medium to the pump 32 stream.

For example, during a warm-up phase, the thermostat blocks 34 the cooler 30 and gives the bypass 36 free, so that the first cooling medium is not through the radiator 30 flow and thus not by means of the cooler 30 is cooled. As a result, the first cooling medium can heat up very quickly, so that the time extension of the warm-up phase can be kept low. However, if the first cooling medium exceeds a predefinable limit temperature, then the thermostat gives 34 the cooler 30 free and obstructs the bypass if necessary 36 so that the first cooling medium through the radiator 30 flows and by means of the cooler 30 is cooled. As a result, excessively high temperatures of the first cooling medium can be avoided. In particular, overheating of the first cooling medium and thus of the internal combustion engine 16 be avoided.

Furthermore, a heating circuit 38 provided, which fluidly with the first cooling circuit 12 is coupled. This allows the first cooling medium the heating circuit 38 flow through and be used for example as a heating medium. For example, at least a portion of the first Cooling circuit 12 flowing through, the first cooling medium, in particular from the cylinder head 20 , branched off and by means of the heating circuit 38 to one in the heating circuit 38 arranged heating 40 be guided. The heating 40 flowing cooling medium is by means of heating 40 heated. In the heating circuit 38 is at least one exhaust aftertreatment device 42 arranged. The present invention is the exhaust aftertreatment device 42 arranged as SCR catalyst (SCR - selective catalytic reduction). This makes it possible, the exhaust aftertreatment device 42 to heat up very quickly by means of the heating medium.

The exhaust aftertreatment device 42 is at least one bypass line 44 of the heating circuit 38 assigned. At least part of the heating medium can bypass the power 44 flow through and thereby the exhaust aftertreatment device 42 handle that so that's the bypass 44 flowing through the heating medium not through the exhaust aftertreatment device 42 flows and thus the exhaust aftertreatment device 42 not heated. Present is in the bypass performance 44 a throttle 46 arranged.

Further, for example, in the first refrigeration cycle 12 a temperature sensor 48 arranged, by means of which a temperature of the first cooling medium can be detected. This makes it possible, for example, the thermostat 34 and / or the pump 32 depending on the means of the temperature sensor 48 operated temperature to operate, in particular to control or regulate.

In addition, in the first cooling circuit 12 a heat exchanger 50 for tempering, that is for cooling and / or heating, a lubricant, in particular a lubricating oil arranged. By means of the lubricant is the internal combustion engine 16 and / or a transmission of the motor vehicle lubricated, so that the heat exchanger 50 Also referred to as engine oil heat exchanger (MÖWWT). At least part of the first cooling medium may be the heat exchanger 50 flow through. Furthermore, the lubricant through the heat exchanger 50 stream. About the heat exchanger 50 can be a heat exchange between the lubricant and the first cooling medium, whereby the lubricant tempered, that is heated and / or cooled, can be. After the heat exchanger 50 becomes the first cooling medium to the collection bar 28 out of which the first cooling medium in the manner described to the thermostat 34 to be led.

The internal combustion engine 16 has two in the Fig. Not shown exhaust gas recirculation devices. A first of the exhaust gas recirculation devices is designed as a high-pressure exhaust gas recirculation device, by means of which a high-pressure exhaust gas recirculation (HP-EGR) can be performed. The second exhaust gas recirculation device is designed as a low-pressure exhaust gas recirculation device, by means of which a low-pressure exhaust gas recirculation (LP EGR) can be performed. For this purpose, the first exhaust gas recirculation device comprises at least one first exhaust gas recirculation line, which at a first branch point fluidly with one of the exhaust gas of the internal combustion engine 16 permeable exhaust tract is connected.

The respective combustion chamber of the internal combustion engine 16 be by means of an intake tract of the internal combustion engine 16 Air and fuel, in particular liquid fuel supplied, so that in the respective combustion chamber, a fuel-air mixture is formed. The fuel-air mixture is burned, resulting in exhaust gas of the internal combustion engine 16 arises. This exhaust gas can flow out of the respective combustion chamber and into the exhaust gas tract, so that the exhaust gas tract can be flowed through by the exhaust gas. The first exhaust gas recirculation line is fluidically connected to the intake tract.

At least part of the exhaust gas flowing through the exhaust tract can be branched off at the first branch point and thus flow into the first exhaust gas recirculation line. By means of the first exhaust gas recirculation line, the exhaust gas flowing through the first exhaust gas recirculation line is returned to the intake tract and introduced into the intake tract. The introduced into the intake exhaust gas is taken by means of the intake air flowing through the air and transported into the combustion chambers.

In the first exhaust gas recirculation line is a first exhaust gas recirculation cooler 52 arranged, which is also referred to as high-pressure exhaust gas recirculation cooler (HP-EGR cooler). By means of the exhaust gas recirculation cooler 52 For example, the exhaust gas flowing through the first exhaust gas recirculation line can be cooled. The second exhaust gas recirculation device comprises at least one second exhaust gas recirculation line, which is fluidically connected to the exhaust gas tract at a second branch point. Further, the second exhaust gas recirculation line is fluidly connected to the intake manifold. Thus, at least part of the exhaust gas flowing through the exhaust gas line can be branched off at a second exhaust gas station, so that the exhaust branched off at the second branching point can flow into the second exhaust gas recirculation line and the second exhaust gas recirculation line can flow through. By means of the second exhaust gas recirculation line, the exhaust branched off at the second exhaust gas station is returned to the intake tract and introduced into the intake tract, so that the introduced exhaust gas is entrained by the air flowing through the intake tract and transported into the combustion chambers.

The second exhaust gas recirculation device also comprises at least one exhaust gas recirculation cooler 54 , which is also referred to as low-pressure exhaust gas recirculation cooler (LP EGR cooler). By means of the exhaust gas recirculation cooler 54 For example, the exhaust gas flowing through the second exhaust gas recirculation line can be cooled.

Here are the exhaust gas recirculation cooler 52 and 54 in the second cooling circuit 14 arranged so that the exhaust gas recirculation cooler 52 and 54 can be flowed through by the second cooling medium. This allows a respective heat transfer from the exhaust gas flowing through the respective exhaust gas recirculation line via the respective exhaust gas recirculation cooler 52 respectively 54 take place to the second cooling medium, whereby the respective exhaust gas flowing through the respective exhaust gas recirculation line is cooled.

Furthermore, in the second cooling circuit 14 at least one pump 56 arranged, by means of which the second cooling medium through the second cooling circuit 14 can be promoted. In addition, in the second cooling circuit 14 at least one temperature sensor 58 arranged, by means of which at least one temperature of the second cooling medium can be detected. This makes it possible, for example, the pump 56 depending on the means of the temperature sensor 58 operated temperature to operate.

Furthermore, the internal combustion engine 16 a charging device 60 on. In the present case, the charging device comprises 60 two turbochargers 62 and 64 so the charging device 60 is designed as a two-stage charging device. Alternatively, it is conceivable that the charging device 60 exactly one exhaust gas turbocharger 62 respectively 64 includes, so that then the charging device 60 is designed as a single-stage charging device.

The respective exhaust gas turbocharger 62 respectively 64 has a turbine arranged in the exhaust tract and can be driven by the exhaust gas. Furthermore, the respective exhaust gas turbocharger comprises 62 respectively 64 a compressor arranged in the intake tract for compressing the air flowing through the intake tract. The respective compressor is of the respective turbine of the respective exhaust gas turbocharger 62 respectively 64 drivable, whereby the air can be compressed by means of the respective compressor. As a result, energy contained in the exhaust gas can be used to compress the air, so that a particularly efficient and fuel-efficient operation of the internal combustion engine 16 is representable.

Relative to the flow direction of the exhaust gas through the exhaust tract is the turbine of the exhaust gas turbocharger 62 for example, upstream of the turbine of the exhaust gas turbocharger 64 arranged. By means of the respective turbine, the exhaust gas is expanded, so that the exhaust gas downstream of the respective turbine has a lower pressure than upstream of the respective turbine. Therefore, the turbine of the exhaust gas turbocharger 62 Also referred to as high-pressure turbine, the turbine of the exhaust gas turbocharger 64 is referred to as a low-pressure turbine. Therefore, the exhaust gas turbocharger 62 referred to as high pressure turbocharger (HD-ATL), wherein the exhaust gas turbocharger 64 is referred to as low-pressure exhaust gas turbocharger (ND-ATL).

The first branch point is based on the flow direction of the exhaust gas through the exhaust tract in front of at least one of the turbines of the turbocharger 62 and 64 arranged, wherein the second branch point after the first branch point and in particular after the at least one turbine is arranged. As a result, the exhaust gas at the first branch point has a higher pressure than at the second branch point, since the exhaust gas is expanded or expanded at least by means of the at least one turbine. Therefore, the first exhaust gas recirculation device is the high-pressure exhaust gas recirculation device, wherein the second exhaust gas recirculation device is the low-pressure exhaust gas recirculation device.

For adjusting the boost pressure of the turbocharger 62 is for example an adjusting device 66 provided, which is designed for example as an electrically actuable adjusting device and is therefore also referred to as e-actuator. Further, for adjusting the boost pressure of the exhaust gas turbocharger 64 for example, an adjusting device 68 provided, wherein the adjusting device 68 may be formed, for example, as an electrically actuated adjusting device and is therefore also referred to as e-controller. Furthermore, in the figure, a bypass line 70 which is provided, for example, and only if the charging device 60 is designed as a single-stage charging device.

From the Fig. It can be seen that the charging device 60 that is the turbocharger 62 and 64 as well as the adjusting devices 66 and 68 in the second cooling circuit 14 is arranged or are. About the bypass 70 is the charging device 60 bypass at least part of the second cooling medium. This means that the bypass line 70 flowing cooling medium not through the charging device 60 flows and therefore not the charging device 60 cools.

The second cooling medium may be from the charging device 60 to the exhaust gas recirculation cooler 54 flow, which thus downstream of the charging device 60 is arranged. From the exhaust gas recirculation cooler 54 can the second cooling medium to the pump 56 flow, from which the second cooling medium finally to the and in particular in the distribution bar 26 can flow. By means of the distribution bar 26 the second cooling medium becomes the exhaust gas recirculation cooler 52 guided, which thus downstream of the distribution bar 26 and in particular the pump 56 and the exhaust gas recirculation cooler 54 is arranged. From the exhaust gas recirculation cooler 52 can the second cooling medium back to the charging device 60 flow, causing the second cooling circuit 14 closed is.

From the Fig. Is also seen that the two cooling circuits 12 and 14 a common reservoir 71 is assigned, by means of which, for example, volume fluctuations of the respective cooling medium can be compensated.

In particular, it is possible for excess cooling medium via respective non-return valves 72 in the expansion tank 71 respectively. It is also possible in the expansion tank 71 absorbed cooling medium the cooling circuit 12 and or 14 supply.

In order to provide a particularly advantageous and needs-based cooling means of the cooling device 10 To realize, it is envisaged that the cooling circuits 12 and 14 fluidly separated from each other, but are interconnected for heat exchange. Further, the pumps 32 and 56 designed as independently operable, electric pumps. In other words, the pumps 32 and 56 designed as electrically operable pumps. The cooling circuits 12 and 14 are thus connected to the heat exchange and can therefore exchange heat, however, the cooling circuits 12 and 14 due to the use of independently operable electric pumps 32 and 56 operated hydraulically or fluidically completely independent of each other, in particular controlled or regulated. For example, both the first cooling medium and the second cooling medium, the distribution bar 26 flow through, so that, for example, via the distribution bar 26 a heat exchange between the cooling media can take place. However, for example, the distribution bar separates 26 the cooling media fluidly from each other, so that, at least in the distribution bar 26 , a fluidic mixing of the cooling media is omitted.

Since the second cooling medium may be formed as a cooling liquid, which is also referred to as cooling water, the pump 56 Also referred to as a water pump. In the present case, the pump 32 a first electrical power, in particular electrical rated power, on, wherein the pump 56 a second electrical power, in particular electrical rated power has. It is provided that the first electrical power is substantially higher than the second electrical power.

By means of the cooling device 10 is a targeted and flexible cooling of the described components in the cooling circuits 12 and 14 at the lowest power consumption feasible. In particular, it is for example during a warm-up of the internal combustion engine 16 possible for the pump 56 is activated while the pump 32 is disabled. Thereby, the recirculated exhaust gas can be cooled while one through the pump 32 causes conveying of the first cooling medium is omitted. This allows the emissions of the internal combustion engine 16 be kept particularly low, at the same time the energy consumption or the energy consumption of the internal combustion engine 16 and thus their fuel consumption can be kept very low.

LIST OF REFERENCE NUMBERS

10

cooling device

12

first cooling circuit

14

second cooling circuit

16

Internal combustion engine

18

crankcase

20

cylinder head

22

second cooling jacket

24

third cooling jacket

26

rail

28

collection strip

30

cooler

32

pump

34

thermostat

36

bypass line

38

heating circuit

40

heater

42

exhaust treatment device

44

bypass line

46

throttle

48

temperature sensor

50

heat exchangers

52

Exhaust gas recirculation cooler

54

Exhaust gas recirculation cooler

56

pump

58

temperature sensor

60

charging

62

turbocharger

64

turbocharger

66

setting device

68

setting device

70

bypass line

71

surge tank

72

check valve

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 102008036277 A1 [0002]
• DE 19960960 C1 [0004]

Claims (5)

Cooling device ( 10 ) for a motor vehicle, with a first cooling circuit through which a cooling medium can flow ( 12 ) in which an internal combustion engine ( 16 ) for driving the motor vehicle, at least one radiator ( 30 ) for cooling the first cooling circuit ( 12 ) flowing through the cooling medium and at least one first pump ( 32 ) for conveying the cooling medium through the first cooling circuit ( 12 ) are arranged, and with a flow-through of a cooling medium second cooling circuit ( 14 ), in which at least one exhaust gas recirculation cooler ( 52 ) and at least one second pump ( 56 ) for conveying the cooling medium through the second cooling circuit ( 14 ) are arranged, characterized in that the cooling circuits ( 12 . 14 ) are fluidly isolated from each other, but are connected to each other for heat exchange, wherein the pumps ( 32 . 56 ) as independently operable, electric pumps ( 32 . 56 ) are formed. Cooling device ( 10 ) according to claim 1, characterized in that in the second cooling circuit ( 14 ) a second exhaust gas recirculation cooler ( 54 ) is arranged. Cooling device ( 10 ) according to claim 2, characterized in that one of the exhaust gas recirculation cooler ( 52 . 54 ) as a low-pressure exhaust gas recirculation cooler and the other exhaust gas recirculation cooler ( 52 ) is designed as a high-pressure exhaust gas recirculation cooler. Cooling device ( 10 ) according to one of the preceding claims, characterized in that in the second cooling circuit ( 14 ) at least one exhaust gas turbocharger ( 62 ), in particular at least two exhaust gas turbochargers ( 62 . 64 ) is arranged. Cooling device ( 10 ) according to one of the preceding claims, characterized in that the first pump ( 32 ) has a higher electrical rating than the second pump ( 56 ) having.

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