DE102009001321A1 - Supercharged internal combustion engine has intake line for supplying internal combustion engine with combustion air and compressor arranged in intake line - Google Patents

Abstract

The supercharged internal combustion engine has an intake line for supplying the internal combustion engine with combustion air and a compressor (1) arranged in the intake line. The compressor has an impeller (4) which is mounted on a rotatable shaft. The compressor has housing (2), in which the impeller is arranged. The compressor is provided with a liquid cooling unit (8), and the housing has an integrated coolant jacket (7,7a). An independent claim is also included for a method for operating a supercharged internal combustion engine.

Description

• – mindestens einer Ansaugleitung zur Versorgung der Brennkraftmaschine mit Verbrennungsluft, und
• – mindestens einem in der mindestens einen Ansaugleitung angeordneten Verdichter, der ein auf einer drehbaren Welle gelagertes Laufrad umfaßt, wobei der Verdichter ein Gehäuse aufweist, in dem das Laufrad angeordnet ist.

The invention relates to a supercharged internal combustion engine with

• - At least one intake passage for supplying the internal combustion engine with combustion air, and
• - At least one arranged in the at least one suction line compressor, which comprises an impeller mounted on a rotatable shaft, wherein the compressor has a housing in which the impeller is arranged.

Of Furthermore, the invention relates to a method for operating a supercharged internal combustion engine of the type mentioned.

in the The term internal combustion engine encompasses the scope of the present invention Diesel engines and gasoline engines, but also hybrid internal combustion engines.

Of the Includes compressor at least according to the invention a rotatably mounted impeller and thus can also be two or several wheels have, if it is designed as a multi-stage compressor, and one or more idlers.

Of the Term "combustion air" is intended to Expressing that it is the case of the compressor or the internal combustion engine supplied gas flow or gas mixture to fresh air, but also with recirculated exhaust gas Enriched fresh air can act, for example, exhaust gas upstream of the compressor is introduced into the suction line. The combustion air is shortened in the context of the present invention also as Called air.

The charge by means of a compressor serves primarily to increase the power of the internal combustion engine. The air required for the combustion process is compressed, which allows each cylinder per cycle more air mass can be supplied. As a result, the fuel mass and thus the mean pressure p _{me can be} increased.

The Charging is a suitable means, with unchanged capacity, the performance to increase an internal combustion engine, or at the same power Reduce displacement. In any case, the charge leads to a increase the space performance and a cheaper Power ground. At the same vehicle boundary conditions can be so the load collective to higher Shifting load ranges in which the specific fuel consumption is lower. The latter is also referred to as downsizing.

The Charging supported hence the constant endeavor in the development of internal combustion engines, fuel consumption to minimize d. H. to improve the efficiency of the internal combustion engine.

at Targeted design of the charge can also have advantages in the Exhaust emissions are achieved. The charge is therefore suitable also to reduce pollutant emissions.

Of the Charging an internal combustion engine and thus the downsizing are but limits set. Thus, the boost pressure ratio of the compressor or the charge pressure which can be generated by means of a compressor is also due to itself in the operation of the internal combustion engine adjusting pollution of Compressor determined and limited.

One essential reason for the pollution of a in an intake manifold of an internal combustion engine arranged compressor is the ventilation of the crankcase of the Internal combustion engine via intake line. The vent should prevent the pressure that is in the crankcase during the Build operation of the internal combustion engine, undesirably high values.

A full Sealing the combustion chambers across from the crankcase can due to the axially movable and guided in cylinder tubes piston can not be ensured, so that part of the fresh cylinder charge or the combustion gases passes into the crankcase and there ensures an increase in pressure.

in the crankcase located oil mixes with those in the crankcase in the form of a fine oil mist Gases, which also originate from the cylinders unburned hydrocarbons contain. supports This is done by getting in the oil sump of the crankcase rotating crankshaft, which contributes to an additional foaming of the oil.

Around the pressure in the crankcase be degraded, according to the prior art method for venting the crankcase used, with the problem of venting consists in particular that in the crankcase located gases with oil and unburned hydrocarbons are contaminated. The out the crankcase exiting vent flow therefore becomes common from those in the vent stream located liquid Ingredients, in particular the oil, separated, for example using a separator.

The thus treated bleed stream, which is not considered to be fully purified and is still contaminated with oil and unburned hydrocarbons, is often added to the schedule introduced suction line of the internal combustion engine and thus fed to combustion.

There to promote the venting stream a pressure gradient is required, the vent flow usually upstream of the compressor introduced into the suction line, where the pressure advantageous is low.

On This way, the venting stream will also passed through the compressor, wherein components of the venting stream, especially oil and unburned hydrocarbons, in the compressor, in particular to the housing walls and the blades of the impeller, deposit. The extent of pollution becomes relevant by the contamination of the venting stream d. H. the concentrations of the relevant components in the vent stream and the prevailing temperatures are determined.

The Change deposits the geometry of the compressor, in particular the flow cross sections, and thus worsen the efficiency of the compressor, the deteriorated efficiency per se, in turn, leads to a higher compression temperature d. H. Outlet temperature leads, the one stronger Pollution feed d. H. promotes pollution.

investigations namely have shown that the outlet temperature of the compressor is the relevant Parameter d. H. the authoritative Influence size for occurrence and the degree of contamination of the compressor is. In addition was found that pollution is largely avoided can, as long as the outlet temperature is a critical temperature does not exceed.

In front In the background of the above, it is an object of the present invention Invention, a supercharged internal combustion engine according to the preamble of claim 1 d. H. of the generic type, with regard to the problem of contamination of the compressor is optimized.

A Another subtask of the present invention is a method to show the operation of such an internal combustion engine.

• – mindestens einer Ansaugleitung zur Versorgung der Brennkraftmaschine mit Verbrennungsluft, und
• – mindestens einem in der mindestens einen Ansaugleitung angeordneten Verdichter, der ein auf einer drehbaren Welle gelagertes Laufrad umfaßt, wobei der Verdichter ein Gehäuse aufweist, in dem das Laufrad angeordnet ist,

die dadurch gekennzeichnet ist, dass

• – der Verdichter mit einer Flüssigkeitskühlung ausgestattet ist, wobei das Gehäuse mindestens einen integrierten Kühlmittelmantel aufweist.

The first subtask is solved by a supercharged internal combustion engine

• - At least one intake passage for supplying the internal combustion engine with combustion air, and
• At least one compressor arranged in the at least one suction line and comprising an impeller mounted on a rotatable shaft, the compressor having a housing in which the impeller is arranged,

which is characterized in that

• - The compressor is equipped with a liquid cooling, wherein the housing has at least one integrated coolant jacket.

The Internal combustion engine according to the invention has a liquid cooled compressor. The Liquid cooling is used to, the outlet temperature of the passed through the compressor and in the compressor to reduce compressed combustion air to to counteract this way of contamination of the compressor or even avoid such pollution.

According to the invention the housing to form a liquid cooling at least an integrated coolant jacket on, so that inherently not only the exit area of the compressor chilled or singular the outlet temperature is lowered, but the temperature also in other parts of the case is lowered. In this respect, the combustion air - depending from the respective embodiment more or less strong - already while the compression in the impeller cooled, with what additional and advantageously to the efficiency of the compressor Influence What happens in connection with a preferred embodiment is explained in more detail.

There an improved d. H. higher Efficiency per se to a lower compression temperature leads, result in synergy effects according to the invention, the above the purely structural measure, namely the Compressor with a liquid cooling to Equip lowering the outlet temperature, go out, and Although in the way that cooling in usually an increase the efficiency conditionally and this higher efficiency from home leads to a lower compression temperature, which is less far away from a predefinable maximum allowable outlet temperature is removed and therefore a lower cooling d. H. Cooling capacity required.

Basically the cooling the compressor or the housing in the form of an air cooling or a liquid cooling are performed. by virtue of the higher one Heat capacity of liquids across from Air can but with the liquid cooling larger amounts of heat dissipated be considered this with air cooling possible is. In addition, there is the possibility an existing coolant circuit a liquid-cooled internal combustion engine or an exhaust gas recirculation for Formation of compressor cooling to use, in particular the coolant pump and the heat exchanger, which lowers the number of components and costs, and a dense one Guaranteed packaging in the engine compartment.

The Liquid cooling of the Compressor requires the equipment of the housing with at least one coolant jacket d. H. the arrangement of the coolant through the housing leading Coolant channels. The Heat does not have to first led to the housing surface be dissipated but is already inside the case the coolant, usually mixed with additives added water. The coolant is doing so by means of a cooling circuit conveyed pump, leaving it in the coolant jacket circulated. The to the coolant released heat is discharged in this way from the interior of the housing and in a heat exchanger the coolant again withdrawn.

With the internal combustion engine according to the invention the first object of the invention is solved, namely a to provide charged internal combustion engine, in terms of the problem of contamination of the compressor is optimized.

Further advantageous embodiments the internal combustion engine are discussed in connection with the subclaims.

Advantageous are embodiments the internal combustion engine, in which the compressor is part of a Exhaust gas turbocharger is.

at an exhaust gas turbocharger are arranged in the intake passage Compressor and provided in an exhaust pipe turbine the same shaft, the turbine hot exhaust gases supplied that relax while releasing energy in the turbine, causing the shaft to rotate. The from the exhaust stream the turbine and finally Energy delivered to the supercharger shaft is also used to drive it used on the loader shaft arranged compressor. The compressor promotes and compresses the combustion air supplied to it, whereby a charge of the internal combustion engine is achieved.

The Advantages of the exhaust gas turbocharger, for example, compared to a Mechanical loader can be seen in that no mechanical connection for power transmission between loader and internal combustion engine is required. While a mechanical one Loader for his drive needed energy Completely from the internal combustion engine, thus the power provided and thus reduces the efficiency, uses the exhaust gas turbocharger the exhaust gas energy of the hot ones Exhaust gases.

Yet can also embodiments of Internal combustion engine be advantageous in which the compressor a mechanical loader is.

at the charging of the internal combustion engine by means of turbocharging that is a noticeable Torque drop observed when falling below a certain speed.

Becomes understandable this torque drop when taking into account that at a Exhaust gas turbocharger, the boost pressure ratio depends on the turbine pressure ratio. For example reduced in a diesel engine, the engine speed or at a Gasoline engine reduces the load, this leads to a smaller exhaust gas mass flow and thus to a smaller one Turbine pressure ratio. This has the consequence that at lower speeds or loads down the boost pressure ratio also decreases, which is synonymous with a torque drop.

One mechanical loader has opposite an exhaust gas turbocharger the main advantage that even at low Speeds are provided a sufficiently high boost pressure can.

The described relationships often lead as well in addition to several to improve the torque characteristic Turbocharger or combinations of turbocharging and mechanical Charging be used. Also, an internal combustion engine according to the invention may have multiple compressors arranged in parallel or in series and either component of an exhaust gas turbocharger or mechanical Loaders are.

Advantageous are embodiments the internal combustion engine, in which the compressor is a centrifugal compressor is. The radial design of the compressor favors d. H. especially simplifies the cooling the combustion air during the compression and that in the way that the to be compressed Combustion air over a large area over a wide area Stretching the radially outwardly extending impeller chilled What can be achieved when using an axial compressor, which is for cooling the Combustion air in the region of the impeller provides only little space, not readily possible is. Nevertheless, an internal combustion engine according to the invention can in principle also be equipped with a compressor in Axialbauweise.

For compressors, reference is made to the direction of outflow from the blades. In the case of a radial compressor, the outflow thus takes place essentially radially. Essentially in this context means that the velocity component in the radial direction is greater than the axial velocity component. The velocity vector of the flow intersects the shaft or axis of the compressor at a right angle if the outflow is exactly radial. The flow can and should preferably axially.

Advantageous are embodiments the internal combustion engine, in which the housing is modular as a multi-part casing is formed and comprises at least two housing segments. To the wheel in the case to be able to place may require a modular and thus demountable design of the housing be.

is the compressor, for example, a centrifugal compressor, are embodiments the internal combustion engine advantageous in which the housing a bearing housing as a first housing segment having, which serves to receive the rotatably mounted shaft, and a compressor housing as a second housing segment has, which is connectable to the bearing housing and also serves to cover the rotatably mounted impeller.

The compressor housing can also be the entry area for an axial flow of the Impeller include d. H. the inlet, through which the combustion air in the case enters and is directed to the wheel. The introduced into the housing Air is flowing along the blades of the centrifugal compressor radially outward. there there is a compression of the combustion air.

There the diameter of the impeller is usually larger than the diameter the entrance opening, the impeller can only be introduced into the housing, if the housing dismountable d. H. modular. The impeller of the in the bearing housing rotatably mounted shaft added d. H. attached to this shaft and by means of a lid-shaped compressor housing covered. In the assembled state of the housing, the bearing housing and the compressor housing connected with each other.

Advantageous are embodiments the internal combustion engine, in which the at least one integrated Coolant jacket arranged in the compressor housing is. Compared to the bearing housing has the compressor housing over the required large-scale expansion and the necessary proximity to the blades of the impeller to the air flow even during the Compression circumferentially cool to be able to.

moreover indicates the compressor housing a big enough one Material volume on to a coolant jacket to integrate in a functional and needs-based way and this coolant jacket in a simple way with coolant from the outside whereas the arrangement of the coolant jacket in the bearing housing constructive highly limited may be difficult or due to other functions of the bearing housing becomes.

To consider is in this context that the compressor housing only the task is to cover the impeller and an entry for the combustion air to provide while the bearing housing in its original d. H. primary Function of the recording of the shaft is used and thus a mechanically highly loaded Part represented by the introduction of coolant channels in his Weakened strength or the integration of coolant channels only in limited Scope allows.

Possibly have to in the bearing housing already Holes for oil supply, especially for lubricating oil supply the shaft bearing, provided and / or forms the bearing housing a part of one opposite the compressor housing arranged turbine housing, which may be the case if the compressor is part of an exhaust gas turbocharger. Often serves the bearing housing also for attachment to the internal combustion engine or to adjacent Components in the engine compartment.

Advantageous are embodiments the internal combustion engine, wherein the at least one integrated in the compressor housing Coolant jacket at least partially follows the contour of the impeller.

Advantageous is this embodiment, because a coolant jacket close to the impeller and the associated cooling of the air during the Compression not only the outlet temperature of the compressed Air lowers, but also increases the efficiency of the compressor, causing in turn reduces the compression temperature.

Advantageous in particular, if the at least one integrated coolant jacket is formed in the way that the combustion air from the beginning the compression on cooled becomes.

at Internal combustion engines in which at least one integrated coolant jacket in the compressor housing is arranged, embodiments are the Internal combustion engine advantageous, which are characterized that at least one additional integrated Coolant jacket in the bearing housing is arranged.

Also if the arrangement of the coolant jacket in the bearing housing for the reasons mentioned above structurally very limited or can be aggravated, increased an additional one Coolant jacket on the opposite side Side of the compressor housing the total cooling capacity the compressor cooling.

In addition, embodiments are conceivable in which the bearing housing has a coolant jacket for other reasons and with Coolant is supplied, for example, if the bearing housing is part of an exhaust gas turbocharger and provided on the opposite side of the compressor turbine via the bearing housing is liquid-cooled. Such a trained bearing housing would offer for the arrangement ie the integration of an additional coolant jacket.

Out the reasons mentioned above can also embodiments the internal combustion engine be advantageous in which the at least an integrated coolant jacket in the bearing housing is arranged.

at Internal combustion engines in which at least one integrated coolant jacket in the bearing housing is arranged, embodiments are the internal combustion engine, which are characterized in that the at least one coolant jacket integrated in the bearing housing arranged on the side facing the impeller of the bearing housing is.

The Efficiency of the liquid cooling can by the arrangement of the at least one integrated in the bearing housing coolant jacket close significantly increased to the impeller be compared to an embodiment in which the coolant jacket not adjacent, but spaced from the impeller and thus to the Compressor air flow is provided.

at Internal combustion engines that are used to form a liquid cooling with a coolant circuit are equipped embodiments be advantageous in which the at least one integrated coolant jacket with the coolant circuit the internal combustion engine is connected. The liquid cooling of the internal combustion engine can the cooling serve the cylinder head or the cylinder block or exhaust gas recirculation or part of a passenger compartment heating and / or oil cooling.

Becomes an already existing coolant circuit a liquid cooling the Internal combustion engine with the at least one integrated in the housing Coolant jacket connected to the compressor associated cooling circuit can be formed, without for this cooling circuit an additional Coolant pump and / or an additional heat exchanger must be provided because already existing and liquid cooling of the Internal combustion engine belonging Aggregates used d. H. can be used. This procedure is reduced the number of components and the cost. In addition, no additional Space takes up d. H. what is needed as possible dense packaging in the engine compartment supported.

It results in a variety of cycle designs. So can one for a passenger interior heating used coolant previously heated in the compressor be, with the combustion air heat is removed.

The at issue embodiment, in the liquid cooling of the Internal combustion engine is used, is particularly suitable for reduction comparatively high compression temperatures of, for example 150 ° C to 190 ° C on lower temperatures above 100 ° C. Because that from the cooling circuit the internal combustion engine for cooling the coolant removed from the compressor has usually even temperatures of 80 ° C and more, and indeed then, if it is the cooling circuit the internal combustion engine, for example, before entering the cylinder head or cylinder block is removed.

insofar the proposed measure is particularly suitable for lowering the outlet temperature at high loads when high compression temperatures generated and expected.

Should the outlet temperature of the compressor even at lower loads and comparatively low compression temperatures of, for example 110 ° C reduced however, are embodiments the internal combustion engine advantageous in which to form a Low-temperature cooling an independent one Coolant circuit is provided, the at least one integrated coolant jacket includes.

With Help of a low-temperature cooling will that be in the case integrated coolant jacket supplied coolant cooled to temperatures of, for example, 30 ° C, 40 ° C or 50 ° C, so that outlet temperatures of 60 ° or 70 ° C can be realized.

Though are such low outlet temperatures to avoid Pollution of the compressor is not required. Temperatures of these Magnitude but are purposeful in improving the efficiency of the compressor, as above already in detail was set out.

The second sub-task underlying the invention, namely to show a method for operating an internal combustion engine according to one of the embodiments described above, is achieved by a method which is characterized in that the liquid cooling of the compressor is operated in such a way that from the compressor or impeller emerging and compressed combustion air does not exceed a predetermined temperature, preferably a temperature of less than 190 ° C, preferably less than 180 ° C.

The Said in connection with the internal combustion engine according to the invention also applies to the inventive method. Optionally, at the outlet of the compressor or at the point of exit the air flow from the blades a sensor for detecting the air temperature intended. Alternatively, the outlet temperature can be determined using simulation models determined d. H. be calculated.

The at the exit from blades of an impeller air temperature is at a predetermined temperature, the maximum allowable outlet temperature acts, compared.

By Lowering the outlet temperature of the compressor by means of liquid cooling can Pollution of the compressor are counteracted, wherein Pollution can be almost avoided as long as the outlet temperature a critical temperature - of for example 190 ° C or 180 ° C - does not exceed.

Advantageous are process variants in which the at least one integrated Coolant jacket in The type is designed and arranged by the compressor pass out Combustion air during the compression cooled becomes.

The cooling of the air during compression not only reduces the outlet temperature of the compressed air, but in particular increases the efficiency of the compressor, which in connection with the description of the 1 is explained in more detail. If compression is considered to be a gradual increase in pressure, cooling the air during compression will result in a lower compression temperature after each incremental pressure increase than in uncooled compression. The lower compression temperature causes a higher density of the compressed combustion air and thus a lower flow rate, which in turn requires a lower compressor power for a discrete increase in pressure, which is why the efficiency increases, since the same size mass flow an equal boost pressure with less compressor work is achieved.

In the following the invention will be described with reference to three embodiments and according to FIGS 1 to 4 described in more detail. Hereby shows:

1 schematically a Ts diagram to illustrate different compression processes with different cooling strategy,

2 a compressor of a first embodiment of the internal combustion engine in half section,

3 a compressor of a second embodiment of the internal combustion engine in half section, and

4 a compressor of a third embodiment of the internal combustion engine in half section.

1 shows a Ts diagram illustrating various compression processes with different cooling strategy, which makes the influence of the cooling and in particular the beginning of the cooling on the outlet temperature, ie the compression end temperature clearly.

On the ordinate the temperature T of the combustion air is plotted in degrees Celsius (° C) and along the abscissa the entropy difference in (kJ / kgK), whereby as a reference state the state ( 1 ) the air at the entrance to the compressor or at the beginning of the compression is used. The isobars form hyperbolas and are registered for pressures between 1 and 3 bar, the increment being 0.5 bar.

If the air supplied to the compressor is not cooled during compression, the air will undergo a state change of state during compression ( 1 ) at the entrance to the impeller to condition ( 2a ) at the exit from the rotor blades, ie along the curve A. By isobaric cooling at 3 bar, the compressed combustion air can then be in the state ( 2 ) are transferred. This procedure is characterized by a high compression end temperature, ie outlet temperature (state ( 2a )) and a low efficiency of the compressor or the compressor.

The cooling the air during The compression not only lowers the outlet temperature of the compressed Air, but increased in particular the efficiency, as the two compression processes along the curves B and C illustrate. In both cases, the compression becomes simplistic as a gradual pressure increase considered.

According to the curve B, the compression is considered as a pressure increase in four steps. After a discrete pressure increase of 0.5 bar, the compressed air is cooled until the entropy increase due to the previous compression is reduced. The air passes through the states 2a ' . 2 B' . 2c ' . 2d ' , The cooling of the air after the fourth and last compression transfers the air into the state 2 , The compression end temperature in the state 2d ' is significantly lower than that in the state 2a , In addition, the state change requires state ( 1 ) in the state ( 2 ) along the curve B a much lower cooling capacity.

According to the curve C is considered the compression as pressure increase in twenty steps. in the Comparison to the process according to curve B is the compression end temperature again lower and the required cooling capacity even lower.

The cooling the air during the compression conditionally - beside the actual compression - one higher Density of combustion air due to heat extraction and thus a lower volume flow, which requires a lower compressor capacity. The efficiency increases as a result of the cooling.

2 shows a compressor 1 a first embodiment of the internal combustion engine in half-section, which is arranged in a suction line for supplying the internal combustion engine with combustion air (not shown).

The compressor 1 is designed in radial design, ie a radial compressor and has an impeller 4 on, on a rotatably mounted shaft and in a housing 2 is arranged. The impeller 4 gets in from the case 2 via entrance area 3 introduced combustion air axially in the direction of the longitudinal axis 9 of the compressor 1 incident flow. The way in the case 2 introduced air flows radially outward along the blades of the centrifugal compressor. In this case, a compression of the combustion air takes place.

The housing 2 of the compressor 1 is modular and includes two housing segments in the present case 2a . 2 B namely, a bearing housing 2 B as a first housing segment 2 B and a compressor housing 2a as a second housing segment 2a , The modular design of the housing 2 is required because the diameter of the impeller 4 greater than the diameter of the inlet area 3 , As part of assembly of the impeller 4 is the case 2 initially in its individual parts ie housing segments 2a . 2 B disassembled. The impeller 4 is mounted on the rotatably mounted shaft and with the cover-shaped compressor housing 2a covered. In the assembled state of the housing 2 are the bearing housing 2 B and the compressor housing 2a connected with each other.

The bearing housing 2 B serves to accommodate the rotatably mounted shaft, whereas the compressor housing 2a primarily to cover the rotatably mounted impeller 4 serves. At the in 2 illustrated embodiment, the compressor housing 2a the entrance area 3 ie this housing segment 2a at the same time forms the entrance area 3 with out.

The compressor 1 is characterized in that it is with a liquid cooling 8th equipped, the housing 2 an integrated coolant jacket 7 . 7a having.

In the present case is the coolant jacket 7 . 7a in the compressor housing 2a integrated and follows advantageously the contour of the impeller 4 , This design and arrangement of the coolant jacket 7 . 7a Creates the necessary proximity to the blades of the impeller 4 to cool the airflow already during the compression. In addition, a large-area cooling is guaranteed, ie a large heat transfer between combustion air and coolant.

The coolant jacket 7 . 7a extends into the diffuser 6 serving exit area 5 , so that the compressed air even after leaving the impeller 4 is cooled.

3 shows a compressor 1 A second embodiment of the internal combustion engine in half section. There are only supplementary comments to the in 2 For this reason, reference is made to FIG 2 and the corresponding description. The same reference numerals have been used for the same components.

The in 3 shown compressor 1 has an additional coolant jacket 7 . 7b which is in the bearing housing 2 B is integrated. This in the bearing housing 2 B integrated coolant jacket 7 . 7b is on the impeller 4 facing side of the bearing housing 2 B arranged and extends in close proximity to the impeller 4 along the impeller 4 into the exit area 5 , The additional coolant jacket 7 . 7b increases the heat transfer between combustion air and coolant and thus contributes to a lowering of the compression end temperature.

4 shows a compressor 1 a third embodiment of the internal combustion engine in half section. It is only supplementary information to the in 2 For this reason, reference is made to FIG 2 and the corresponding description. The same reference numerals have been used for the same components.

Unlike the in 2 illustrated embodiment, the in 4 shown compressor 1 over two in the compressor housing 2a integrated coolant jackets 7 . 7b ,

A first coolant jacket 7 . 7a is in close proximity to the blades of the impeller 4 arranged and follows the contour of the impeller 4 or extends along the contour of the impeller 4 , This first coolant jacket 7 . 7a ensures cooling of the air during compression.

In addition, a second coolant jacket 7 . 7a near the exit area 5 provided with the impeller 4 compressed air 7 . 7a even after leaving the wheel 4 is cooled further.

Also in 4 illustrated embodiment can with an additional coolant jacket in the bearing housing 2 B be supplemented or combined.

1

compressor

2

casing

2a

Compressor housing, housing segment

2 B

Bearing housing, housing segment

3

entry area

4

Wheel

5

exit area

6

diffuser

7

Coolant jacket

7a

Coolant jacket in the compressor housing

7b

Coolant jacket in the bearing housing

8th

liquid cooling

9

longitudinal axis

Claims (15)

Supercharged internal combustion engine with - at least one intake line for supplying the internal combustion engine with combustion air, and - at least one compressor arranged in the at least one intake line ( 1 ), which is a mounted on a rotatable shaft impeller ( 4 ), wherein the compressor ( 1 ) a housing ( 2 ), in which the impeller ( 4 ), characterized in that - the compressor ( 1 ) with a liquid cooling ( 8th ), the housing ( 2 ) at least one integrated coolant jacket ( 7 . 7a . 7b ) having. Supercharged internal combustion engine according to claim 1, characterized in that the compressor ( 1 ) Is part of an exhaust gas turbocharger. Supercharged internal combustion engine according to claim 1, characterized in that the compressor ( 1 ) is a mechanical loader. Supercharged internal combustion engine according to one of the preceding claims, characterized in that the compressor ( 1 ) is a radial compressor. Supercharged internal combustion engine according to one of the preceding claims, characterized in that the housing ( 2 ) modular as a multi-part housing ( 2 ) is formed and at least two housing segments ( 2a . 2 B ). A supercharged internal combustion engine according to claim 5, wherein the compressor ( 1 ) is a radial compressor, characterized in that the housing ( 2 ) a bearing housing ( 2 B ) as a first housing segment ( 2 B ), which serves to receive the rotatably mounted shaft, and a compressor housing ( 2a ) as a second housing segment ( 2a ), which with the bearing housing ( 2 B ) is connectable and also to cover the rotatably mounted impeller ( 4 ) serves. Supercharged internal combustion engine according to claim 6, characterized in that the at least one integrated coolant jacket ( 7 . 7a ) in the compressor housing ( 2a ) is arranged. Supercharged internal combustion engine according to claim 7, characterized in that the at least one integrated coolant jacket ( 7 . 7a ) at least partially the contour of the impeller ( 4 ) follows. Supercharged internal combustion engine according to claim 7 or 8, characterized in that at least one additional integrated coolant jacket ( 7 . 7b ) in the bearing housing ( 2 B ) is arranged. Supercharged internal combustion engine according to claim 6, characterized in that the at least one integrated coolant jacket ( 7 . 7b ) in the bearing housing ( 2 B ) is arranged. Supercharged internal combustion engine according to claim 9 or 10, characterized in that the at least one in the bearing housing ( 2 B ) integrated coolant jacket ( 7 . 7b ) on the impeller ( 4 ) facing side of the bearing housing ( 2 B ) is arranged. Supercharged internal combustion engine according to claim 11, characterized in that the at least one in the bearing housing ( 2 B ) integrated coolant jacket ( 7 . 7b ) along the impeller ( 4 ). Supercharged internal combustion engine according to one of the preceding claims, which is equipped to form a liquid cooling with a coolant circuit, characterized in that the at least one integrated coolant jacket ( 7 . 7a . 7b ) is connected to the coolant circuit of the internal combustion engine. Supercharged internal combustion engine according to one of claims 1 to 12, characterized in that for the formation of a low-temperature cooling, an independent coolant circuit is provided, which comprises the at least one integrated coolant jacket ( 7 . 7a . 7b ). Method of operating a charged Internal combustion engine according to one of the preceding claims, characterized in that the liquid cooling ( 8th ) of the compressor ( 1 ) is operated in the way that from the impeller ( 4 ) and compressed combustion air does not exceed a predetermined temperature.