WO2006045488A1

WO2006045488A1 - Condenser in a turbo-compressor system and method for operating one such system

Info

Publication number: WO2006045488A1
Application number: PCT/EP2005/011188
Authority: WO
Inventors: Jochen Eitel; Gerhard FRÄNKLE; Peter Geskes; Rainer Lutz; Rolf Müller; Eberhard Pantow
Original assignee: Behr Gmbh & Co. Kg
Priority date: 2004-10-25
Filing date: 2005-10-18
Publication date: 2006-05-04
Also published as: US20080028757A1; EP1825130A1

Abstract

The invention relates to an system, especially a turbo-compressor system pertaining to a motor vehicle comprising an internal combustion engine with exhaust gas recirculation. Said system comprises an exhaust gas cooler (2) and a charge-air cooler (L) for cooling recirculated exhaust gases and/or charge air, a compressor (V) for compressing the charge air, and at least one condenser (3).

Description

) ND ENSATABS CHEIDER ICT OF A TURBOCHARGER ARRANGEMENT AND METHOD OF OPERATION: NON SUCH ANORDNUCTG

The invention relates to a turbocharger arrangement and a method for operating a turbocharger according to the preamble of claim 1 or claim 19.

To reduce the particle and nitrogen oxide emissions in diesel engines, the return of exhaust gas is known, with both a high-pressure exhaust gas recirculation and a low-pressure exhaust gas recirculation is possible. In this case, the exhaust gas stream is cooled to temperatures of about 15O ⁰ C to 200 ⁰ C and admixed with the intake air. As a cooling medium in the exhaust gas cooler at these temperatures, the cooled intake air usually a partial flow of the engine coolant is used, but also the use of other coolant is known. Exhaust gas recirculation is all the more effective the lower the gas outlet temperatures at the exhaust gas cooler are.

In the case of high-pressure exhaust gas recirculation, exhaust gas is usually taken off in front of the turbine and the charge air is supplied to the charge air cooler. The cooling of the recirculated exhaust gas takes place by the hot engine coolant, so that due to the high temperatures usually no Exhaust gas condensate is formed. High-pressure exhaust gas recirculation achieves a significant reduction in nitrogen oxide emissions, but with a simultaneous increase in particulate emissions. The particle or particulate matter emission can be reduced by particle filters.

In the case of the low-pressure exhaust gas recirculation, the exhaust gas is removed after the turbine, preferably after a particle filter, taken from the exhaust gas flow, cooled and fed to the compressor on the suction side. Due to the greater cooling of the recirculated exhaust gas, a further reduction of the nitrogen oxide emission is possible, however, forms due to the strong cooling of the recirculated exhaust gas condensate, which is sour starK, which essentially goes back to the formed nitric acid HNO ₃ , so that it Corrosion comes. If condensate mist is fed to the compressor, it can also damage the compressor because of its high speed (about 120000 to 150000 rpm).

In commercial vehicles, in addition to the exhaust gas recirculation to reduce the nitrogen oxide emission and the SCR process (Selective Catalytic Reduction) is known in which ammonia is produced either from ammonium carbamate or aqueous urea solution, which catalytically converts the nitrogen oxide generated by the engine into the harmless components nitrogen and water , However, this method has the disadvantage dsss an additional fuel must be carried in the vehicle.

Based on this prior art, it is an object of the invention to provide an improved turbocharger arrangement and a method for operating a turbocharger, in which the risk of corrosion is as low as possible. This object is achieved by a turbocharger arrangement and a method having the features of claim 1 and of claim 19. Advantageous refinements are the subject of the claims. In the following, the term "charge air" is understood to mean both the intake air and the intake air mixed with the recirculated exhaust gas.

According to the invention, a turbocharger arrangement, in particular a motor vehicle with an internal combustion engine, is provided with exhaust gas recirculation, the arrangement having an exhaust gas cooler and a charge air cooler for cooling recirculated exhaust gas and / or charge air and a compressor for compressing the charge air and a condensate separator. By means of the condensate separator, the corrosive fraction of the exhaust gas located in the condensate, which forms when the dew point temperature is reached and reached, can be removed from the exhaust gas stream or the charge air stream and ensured that no or only minimal condensate occurs in the following region collects, which promotes an eventual corrosion of the components. The condensate separator is hereby preferably arranged directly after the cooler for cooling the recirculated exhaust gas and / or after the charge air cycle here and / or directly in front of the charge air compressor.

The condensate separator may preferably be a centrifugal or cyclone separator. Alternatively, it is also possible to use another turbulence generator, which conveys condensate droplets located in an air flow to the outside, so that they can be discharged. Any other equivalent devices are also possible.

Furthermore, the use of a filter, for example made of stainless steel or plastic fabric or fleece, which serves as a condensate separator, is possible. - A -

In all cases, the condensate separation can be done in several stages to increase the effectiveness. Different condensate separators can be combined as required.

To the condensate from a collection o.a. A valve for throttling the exhaust gas flow or the charge air flow is preferably provided so that the pressure level can be raised and the condensate can be discharged without additional aids. Alternatively, the use of tools, such as a pump or other arrangement, which allows a temporary increase in pressure Sammelbe¬ container possible.

At the condensate drain, a check valve may be provided which allows outflow of the condensate, but prevents backflow of condensate and / or air from the outside.

Furthermore, the condensate drain can have such a discharge gradient that the weight force on the condensate corresponds at least to the suction pressure, so that a suck back of condensate can be prevented.

The condensate separator is preferably arranged directly downstream of the cooler, in particular directly downstream of the exhaust gas cooler. Also, an arrangement after the intercooler is useful. In order to protect the compressor against damage by condensate droplets, an arrangement directly in front of the compressor is also expedient. In this case, the shaft of the compressor can advantageously be used as drive or part of a centrifugal separator.

The condensate separator must also be arranged in an area in which condensate droplets are present. This is usually the case in an area in which the temperature of the exhaust gas stream or of the exhaust gas stream Charge air flow to the dew point (taking into account the other parameters, in particular pressure and chemical composition) reaches or falls below.

According to the invention, the exhaust gas or the charge air is in a region in which the exhaust gas or the charge air has a temperature which corresponds to the dew point or falls below the same deflected, in particular beauf¬ with a velocity component in the tangential direction, so that preferably the longitudinal movement a Rotationsbeweg is superimposed, but also a deflection of the air flow can be sufficient. Due to the velocity component in the tangential direction, the forming condensate droplets are moved outward and can be deposited on the wall, from where they can collect, be forwarded and discharged. In the region of the condensate separation, the average tangential velocity component is preferably at least as great as the mean velocity component in the longitudinal direction, preferably at least twice as large.

The Kondensatabscheider is preferably coupled to the shaft of the compressor or fixed, so that a high speed with little design effort and without additional drive is possible.

The condensate separator preferably has a displacer or Schleu derkörper, which is rotatably mounted on the shaft or formed by a Be¬ rich the shaft. This follower body is preferably made of a light metal or a light metal alloy, such as aluminum, titanium or magnesium, or made of a plastic. Alternatively or additionally, it may have a surface coating, for example an oxalic layer, which protects it from corrosion. The body is vorzugs¬ wise fluidically designed such that it despite the deflection no turbulence generated. Furthermore, it is minimized in terms of its mass to avoid mass forces.

The displacer or spinner is preferably arranged in the normal flow direction of the charge air upstream of the impeller of the compressor and preferably directs the charge air flow by at least 90 °, preferably by two times 180 °. In particular, a Z-type deflection by z-about 180 ° leads to a very good separation of the condensate drops, with a part of the condensate drops knock off the body and thrown from there as a result of centrifugal force to the inner channel or housing wall. In this case, the kinetic energy of the condensate drops can be used for removing the condensate from the interior.

The condensate separator is preferably arranged in the compressor housing and / or integrated in the compressor housing. The compressor housing preferably has bores for the condensate drain.

Preferably, the assembly includes a thermal condensate removal which enables detoxification of the condensate, so that acid, the acids condensate in Kon¬ contained, in particular the nitric acid, the sulfuric and are converted into their non-hazardous gases and ^"water, the sulfurous acid. This can then be added to the exhaust gas and delivered to the environment via the exhaust.

The thermal condensate removal is preferably multi-stage, in particular three-stage, formed. As a first stage, an exhaust-heated heat exchanger for heating the condensate is preferably provided. As a second stage, a thermal reactor is preferably provided, which preferably comprises a PTC heating element and regulates automatically when no condensate is obtained. As a third stage, preferably further thermosohermal reaction Actuator provided for a Resterhitzung, in particular in the form of a elektri¬'s radiator, which heats the vaporized condensate to 350 to 450 ^c C, so that the nitric acid vapor on its innocuous Comp components nitrogen, water and oxygen converts. In particular in the thermal reactor of the third stage, internals are preferably provided for increasing the surface area so that the chemical process sequence can be optimized. It can be provided for each Kondensatabscheider a thermal condensate sat entsorgung, but preferably a common condensate disposal is provided for several Kondensatabscheider.

The heating of the thermal condensate removal may preferably be at low operating temperatures (122 ° C), the lead ₂ formation of NO, are operated getak¬ tet, to allow, for example, load-dependent metering of NO ₂ so that the NO x limits to be met.

Likewise, an additional blower can be provided, which ensures egg conservation of the MAK values, irrespective of the function of the condensate discharge.

Preferably, lines are provided between the condensate separator and the condensate removal line, which lines have an automatic conveying effect as a result of capillary forces and / or their arrangement, so that pumps can be dispensed with.

In the following, turbocharger arrangements will be explained in detail with reference to several exemplary embodiments with reference to the drawing. Show it:

1 is a schematic diagram of a Vorricrrtung for cooling exhaust gas, as it can be used in a turbocharger assembly according to the invention, 2 is a schematic view of a first Ausführungsbei¬ game,

3 is a schematic view of a second embodiment,

4 is a schematic view of a third embodiment,

5 is a schematic view of a fourth Ausführungsbei¬ game,

6 is a schematic view of a fifth Ausführungsbei¬ game,

7 is a schematic representation of a turbocharger arrangement with high-pressure exhaust gas recirculation,

8 is a schematic representation of a turbocharger arrangement with low-pressure exhaust gas recirculation,

Fig. 9 is a schematic view of a seventh Ausführt! example with a first variant of a centrifugal separator,

10 is a schematic view of an eighth Ausführu ngsbei¬ game with a second variant of a centrifugal separator,

11 is a schematic representation of a turbocharger arrangement with low-pressure exhaust gas recirculation with two-stage cooling of the recirculated exhaust gas, 12 shows a schematic representation of a turbocharger arrangement with low-pressure exhaust gas recirculation with thermal condensate disposal, and

13 shows a schematic detail of the thermal condensate disposal of FIG. 12.

Fig. 1 shows a small section of a turbocharger arrangement. In this case, a device 1 for cooling recirculated exhaust gas of a power tool is shown with an internal combustion engine which has a condensate separator 3 arranged downstream of a coolant-cooled exhaust gas cooler 2 with an exhaust gas outlet 4 and a condensate outlet 5. In Fig. 1, the flow direction of the exhaust stream is indicated by arrows. The function, as well as that of Ausführungs¬ Examples 1 to 5 described below is in each case the same, namely by the Abgas¬ cooler 2 to about 150 ⁰ C (temperature below dew point, taking into account the other parameters, in particular pressure and chemical Zusam¬ composition) cooled exhaust gas flow, the moisture is removed by the condensate 3 as far as possible directly after exiting the exhaust gas cooler 2. The dry exhaust gas flow passes via a dip tube 6 from the condensate 3 and is then mixed with the intake air. The resulting charge air flow is further compressed, cooled in the intercooler and then fed to the turbocharger (not shown).

In the present case, the recirculated exhaust gas stream has passed through a particle filter before the branching off of the exhaust gas stream, so that as far as possible no particles, in particular no larger particles, are separated off in addition to the condensate, which deposits and thereby reduces the maintenance effort. increase wall. However, especially small particles can serve as condensation seeds and have a positive effect on the condensation.

The deposition of the condensate droplets according to the following five embodiments takes place in the condensate separator 3 by a Ver¬ settlement of the exhaust gas flow in rotation, so that the condensate droplets are not only taken in the axial direction of the exhaust stream but insbesonde¬ re also conveyed to the outside and largely accumulate on the wall, from where they can descend due to gravity down and can be dissipated. The pressure loss through the condensate 3 is relatively low. As a result of the deposition of the aggressive condensate, the components arranged behind are protected, so that the risk of corrosion can be significantly reduced.

According to the first exemplary embodiment illustrated in FIG. 2, a centrifugal force separator which is conventional in principle is provided as condensate deflector 3, which is part of the device 1. As a result of gravity, the precipitate condensate flows down through the condensate outlet 5, where an opening is arranged with a collecting container 7, in which the condensate is collected. The collecting container 7 Λ / vird if allowed to emptied. It should be noted that there is a negative pressure compared to the environment, so that the condensate must be sucked n, so far no Druckhi, for example, by stopping the A-bgasstroms takes place. A detailed description of possible centrifugal shut-off eider takes place later with reference to Figures 9 and 10th

In order to effect an increase in pressure, a shut-off valve 8 arranged in the exhaust gas flow is provided according to the second exemplary embodiment shown in FIG. If the condensate to be removed, the Absperr¬ valve 8 is short-circuited, so that the pressure in the device increases and the condensate can drain off. It can be stored in a collecting container (not shown) until it is emptied.

According to the third exemplary embodiment shown in FIG. 4, which substantially corresponds to the first exemplary embodiment, a pump 9 is arranged downstream of the collecting container 7, which pump is automatically actuated when a certain filling level of the collecting container 7 is reached, so that, in particular in the case of a low pressure Exhaust gas recirculation, which is connected to a pressure below the ambient level, no stopping of the exhaust gas flow as in the second embodiment erforder¬ is required to raise the negative pressure in the collecting container 7 to ambient level.

A further possibility of an increase in pressure in the collecting container 7 is according to the fourth embodiment shown in FIG. 5 the provision of two valves 10 at the condensate inlet and condensate outlet thereof and a thin tube 11 with a regulating valve 12 which connects the collecting container 7 to the high-pressure side of the charge air line , so that when opening the control valve 12, the valve 10 is automatically closed at Konden¬ sateinlass, the pressure in the collecting container 7 increases and upon reaching a pressure level increased relative to the environment, the second valve 10 opens automatically at the condensate outlet, so that the Kon¬ condensate dissipated can be.

Of course, other variants for increasing the pressure in the reservoir are possible to dissipate the condensate.

According to the fifth exemplary embodiment illustrated in FIG. 6, a turbulence generator 13 is integrated in the line downstream of the exhaust gas cooler 2 in conjunction with a downstream annular channel 14 as condensate separator 3. By the turbulence generator 13, the exhaust gas stream with a Superimposed on rotational movement, so that in turn the condensate droplets forming on the basis of the reduced temperature after the exhaust gas cooler 2 are carried to the outside and deposited on the wall. Due to the speed component of the exhaust gas flow in the longitudinal direction, the condensate is entrained in the longitudinal direction and thus enters the channel 14, where it is discharged downwards and collects in a collecting container 7 according to the first embodiment. For emptying the collecting tank 7, in particular in the case of low-pressure exhaust gas recirculation, measures according to the embodiments described above are possible, for example.

The arrangement of the condensate separator does not necessarily have to be directly downstream of the exhaust gas cooler. For example, an arrangement after a subsequent intercooler is useful, especially if the temperature only reaches or falls below the dew point, so that in this case the charge air is cooled, which consists of de r intake air and the recirculated exhaust gas. Accordingly, in principle, the pure intake air can be dried.

According to a sixth exemplary embodiment not shown in the drawing, a filter according to the exhaust gas cooler, which has a synthetic fleece, is arranged as a condensate separator. The condensate forming thereon collects and runs downwards, where it is collected in a collecting container.

FIGS. 7 and 8 show examples of a possible arrangement of a condensate separator 3 in the case of high-pressure exhaust gas recirculation (FIG. 7) and in the case of low-pressure exhaust gas recirculation (FIG. 8). In this case, the configuration can be made in all cases according to the embodiments described above. The lines of Nieder¬ pressure side are in Figures 7 and 8 by thick solid lines shown, the high pressure side by dashed lines. The Strömungs¬ directions are each illustrated by arrows.

According to the high-pressure exhaust gas recirculation shown in FIG. 7, the diversion of the exhaust gas to be recirculated takes place from the exhaust gas flow coming from the engine M on the high-pressure side, ie before a pressure reduction. The intake air is compressed in a compressor V, flows through a charge air cooler L, and is then supplied with the recirculated, cooled exhaust gas 3, which is dry after flowing through the condensate separator 3. Subsequently, the charge air flow is fed to the engine M.

8 shows an example of a low-pressure exhaust gas recirculation, wherein the exhaust gas to be recirculated is branched off from the exhaust gas flow coming from the engine M on the low-pressure side, that is to say after a pressure reduction. In order not to damage the compressor V and the subsequent charge air cooler L and to protect it from corrosion, it is guided through the exhaust gas cooler 2 and the condensate separator 3 and only then supplied to the intake air. The charge air flow, which is now formed by the recirculated exhaust gas and the intake air, is cooled in the intercooler L and fed to the engine M.

In order to avoid the mass flow dependence and the additional installation depth of a cyclone separator required for the installation, according to the seventh and eighth exemplary embodiments, a centrifugal separator with a rotating displacer or spinner 20 can be provided as condensate separator 3, in which case the displacer or spinner 20 on the elongated shaft 21 of the turbocharger, on which the compressor wheel 22 is arranged, is mounted before entering the Ver¬ denser V. In this way, the rotational speed of the centrifugal separator is coupled to the rotational speed of the compressor impeller 22, which is generally from 120,000 to 150,000 rpm. The condensate drop leading Charge air flow impinges on the displacer or spinner 20, so that a deflection of the flow is forced, so that a large part of the condensate droplets are deposited on the displacer or spinner 20 and thrown outwards by the latter as a result of the high speed, where they are collect and flow in the direction of condensate drain 5. The deflection of the charge air flow due to the displacer or Schleuder¬ body 20 in conjunction with the compressor inlet is geometrically designed here so that more condensate drops are deposited, which have not deposited on the displacement or spinner 20.

According to the seventh exemplary embodiment for a condensate separator shown in FIG. 9, the displacer or spinner 20 is cup-shaped, the opening pointing in the direction of the compressor V. Due to the Z-like deflection of the charge air flow, in this case by 2 x about 180 °, wer¬ the most condensate drops deposited before the charge air enters the compressor V. The presently made of an aluminum alloy displacer or spinner 20 is inserted end auf¬ on the shaft 21 and soldered to the same.

10 shows a displacer or spinner 20 for a radial condensate discharge according to the eighth exemplary embodiment of a condensate separator 3. In this case, the air is deflected outwards by approximately 90 °, so that the condensate droplets are displaced onto the displacer or spinner meet body 20 from which they are hurled due to the centrifugal force with high kinetic energy to the outside in an annular condensate drain leading to the channel 5, which has a schematically indicated Ven¬ tilmechanismus 23, which auf¬ the high kinetic energy auf¬ striking condensate lets through, but prevents condensate backflow into the compressor chamber. The presently made of plastic displacer or spinner 20 is inserted end auf¬ on the shaft 21 and glued to the same, with as additional security, the Wei- lenende have a hexagonal shape and the displacer or Schleuder¬ body 20 have a corresponding inner shape.

FIG. 11 shows a low-pressure exhaust gas recirculation with two-stage cooling of the recirculated exhaust gas (exhaust gas cooler 2) in addition to the (presently) one-stage charge air cooling (charge air cooler L). In this case, the exhaust gas coming from the engine M flows through the turbine T and, in the relaxed, cooled state, a subsequently arranged filter F is removed from the exhaust gas by means of its particles. Valve-controlled, a part of the exhaust gas purified by particles can be recirculated at a branch, the remainder of the exhaust gas passes through the exhaust to the outside. In this case, the exhaust gas recirculation quantity is determined by the settling pressure gradient of exhaust back pressure and intake negative pressure, so that high exhaust gas recirculation quantities are possible with simple means.

The recirculated part of the exhaust gas is passed through a two-stage exhaust gas cooler 2, wherein in the first stage 2 'a pre-cooling by the engine coolant, which circulates in an otherwise conventionally designed engine cooling circuit, takes place. If necessary, the exhaust gas temperature is further reduced in the second stage 2 ", while the second stage 2" is part of a low-temperature cooling circuit. This has an air-cooled Niedertem¬ temperature cooler NK, which is arranged in the air stream following the motor coolant cooling high-temperature radiator HK, a compressor K for circulating the coolant or refrigerant and in parallel branches a charge air cooler L and the second stage. 2 of the exhaust gas cooler 2, wherein the cooling or refrigerant distribution is controlled by means of valves.

Further, for the charge air flow or a part thereof, a valve-controlled if necessary available bypass B is provided, which runs parallel to the engine N / 1 and charge air can lead past the same. 11, after the second stage 2 "of the exhaust gas cooler 2, a condensate separator 3 is provided, with the aid of which condensate can be removed from the cold recirculated exhaust gas before it is mixed with the fresh air sucked in. In the present case, though not shown in more detail - arranged directly upstream of the compressor V a further condensate, in particular a centrifugal separator as described above with Bezugnah¬ me to the figures 9 or 10.

For disposal of the accumulating condensate, which is classified as hazardous substance and therefore can not be stored on board a vehicle, a thermal condensate discharge 30 is provided. In this case, the acids formed can be converted into non-critical components with the aid of a multi-stage thermal reactor. In addition, the condensate formed can be used for the precooling of the recirculated exhaust gas.

An example of the arrangement of such a condensate discharge 30 in ei¬ ner low-pressure exhaust gas recirculation is shown schematically in Figures 12 and 13. Here, condensate, which collects on the exhaust gas cooler 2, in front of the compressor V and in or after the charge air cooler L via lines gene to a central condensate collector 31 out of which it is fed via a line to a thermal reactor 32, the part of thermal condensate discharge 30 is. The thermal reactor 32 is subsequently integrated with the filter F in an exhaust manifold of the engine. The condensate-carrying lines, in particular the Lei¬ tion from the condensate collector 31 to the thermal reactor 32, vor¬ lying on a cross section, which allows a promotion of the condensate due to capillary forces, so that can be despised on pumps. In addition, in the present case there is no essential storage of the resulting condensate in the engine system, but the condensate is disturbed. directly passed to the thermal reactor 32, heated therein and then discharged.

As can be seen from FIG. 13, the condensate is used in a first stage S1 for cooling the recirculated exhaust gas, for which purpose a correspondingly formed heat exchanger forms the first stage 2 'of the exhaust duct 2, ie is arranged before the actual exhaust gas cooler 2 enters that substantially the entire enthalpy change of the condensate can be used for the first stage S 1 of the cooling of the exhaust gas. This causes a heating of the condensate. For good heat transfer, ribs or corresponding measures which increase the surface area are provided for optimizing the heat transfer of the exhaust gas heat to the condensate.

In a second step S2, the evaporation of the heated Konden¬ sats, whereby the further heating presently follows er¬ by means of a self-regulating PTC-Heizelernents (Positive Thermal Coefficient) to about 250 to 300 ⁰ C, and takes place in a third step S3, a Reheating to 350 to 450 ⁰ C. In this case, regardless of the engine operating condition sufficient energy is available to operate the PTC heating element. Furthermore, the PTC heating element is designed such that it automatically stops when no condensate has accumulated. The Resterhitzung the evaporated condensate in the third stage is carried out in the present case by means of an electrically heated Rohr¬ heater, which has a surface temperature of 350 to 450 ° C and Einbau¬ th or packing with a large surface area and possibly catalytic action.

Owing to the temperatures of the second and third stages S2 and S3, nitric acid decomposes into NO ₂ , N ₂ , H ₂ O and O ₂ and sulfuric acid or sulfurous acid in H ₂ O and SO ₂ or SO ₃ according to the following reactions: 4 HNO ₃ -> 4 NO ₂ + 2 H ₂ O + O ₂ 4 HNO ₃ -> 2 N ₂ + 2 H ₂ O + 5 O ₂ H ₂ SO ₄ -> SO ₃ + H ₂ OH ₂ SO ₃ -> SO ₂ + H ₂ O

After the third stage S3, the now harmless condensate is fed to the exhaust gas stream and disposed of via the exhaust.

To ensure that no impermissible MAK values occur, an additional blower can be provided, which ensures compliance with the limit values regardless of the function of the condensate discharge 30.

Claims

Patent claims

1. Arrangement, in particular turbocharger arrangement of a motor vehicle with an internal combustion engine, with exhaust gas recirculation, the An¬ order an exhaust gas cooler (2) and a charge air cooler (L) for Küh¬ treatment of recirculated exhaust gas and / or charge air and a compressor (V) for compression having the charge air, characterized in that the arrangement comprises at least one condensate separator (3).

2. Arrangement according to claim 1, characterized in that the Kon¬ densatabscheider (3) is a centrifugal or Zyklonabscheider.

3. Arrangement according to claim 1 or 2, characterized in that the Kondensatabscheider (3) has a turbulence generator (13) which sets the exhaust stream or the charge air flow in rotation, so that at least a portion of the condensate droplets deposited on the wall.

4. Arrangement according to claim 3, characterized in that after the turbulence generator (13) an annular channel (14) is arranged with an outlet opening for the condensate.

5. Arrangement according to claim 1, characterized in that the Kon¬ densatabscheider (3) is a filter.

6. Arrangement according to one of the preceding claims, characterized ge indicates that a multi-stage condensate separation is vorgese¬ hen.

7. Arrangement according to one of the preceding claims, characterized ge indicates that the condensate drain (5) a collecting container (7) is arranged.

8. Arrangement according to one of the preceding claims, characterized ge indicates that a valve (8) is provided for throttling the bvbgasstroms or the charge air flow.

9. Arrangement according to one of the preceding claims, characterized ge indicates that a pump (9) is provided for sucking the collected condensate.

10. Arrangement according to one of the preceding claims, characterized ge indicates that the Kondensatabscheider (3) is arranged directly after the Küh¬ ler, in particular the exhaust gas cooler (2).

11. Arrangement according to one of the preceding claims, characterized ge indicates that the Kondensatabscheider (3) is arranged in an area an¬, in which the temperature of the exhaust gas stream or the charge air flow reaches or falls below the dew point.

12. Arrangement according to one of the preceding claims, characterized ge indicates that the condensate (3) with the shaft (21) of the compressor (V) is coupled or firmly connected.

13. Arrangement according to claim 12, characterized in that the Kon¬ densatabscheider (3) has a positive displacement or centrifugal body (20) which is rotatably mounted on the shaft (21) or formed by a portion of the shaft (21).

14. Arrangement according to claim 13, characterized in that the displacer or spinner (20) in the normal flow direction of the charge air in front of the impeller (22) of the compressor (V) is arranged and the charge air flow by at least 90 °, preferably by two times 180 ° , diverts.

15. Arrangement according to one of claims 12 to 14, characterized gekenn¬ characterized in that the Kondensatabscheider (3) arranged in the compressor housing and / or is formed integrally integrated into the compressor housing.

16. Arrangement according to one of the preceding claims, characterized ge indicates that the arrangement has a thermal Kondensatentsor¬ supply (30).

17. Arrangement according to claim 16, characterized in that the thermal condensate discharge (30) is formed in multiple stages.

18. Arrangement according to claim 16 or 17, characterized in that the thermal condensate discharge (30) with several Kondensatab¬ separators (3) is connected via lines.

19. A method for operating a turbocharger, in particular a motor vehicle with an internal combustion engine, in which exhaust gas recirculates and the charge air is added, characterized in that the exhaust gas or the charge air in a region in which the exhaust gas or the charge air Temperature which corresponds to the dew point or falls below the same, is deflected or passed through a filter ter.

20. The method according to claim 19, characterized in that the flowing substantially in a straight line exhaust stream or the air flow in an area directly after a Küh ler, in particular ei¬ NEM exhaust gas cooler, deflected or passed through the filter.

21. The method according to claim 20, characterized in that the beat with a velocity component in the tangential direction beauf¬, so that the longitudinal movement is superimposed on a rotational movement.

22. The method according to any one of claims 19 to 21, characterized gekennzeich¬ net, that the average tangential velocity component at least as large as the average velocity component in the longitudinal direction.

23. The method according to any one of claims 19 to 22, d adurch gekkezeich¬ net, that the average tangential velocity component at least twice as large as the average Geschwindigkeitskompo¬ nent in the longitudinal direction.

24. The method according to any one of claims 19 to 23, d adurch gekennzeich¬ net that on a positive displacement or centrifugal body (20) sam¬ melndes condensate is thrown by centrifugal force to the outside.

25. The method according to any one of claims 19 to 24, characterized gekennzeich¬ net, that the condensate by means of a thermal Kondensatentsor¬ supply (30) is evaporated, the acids contained in the condensate um¬ converted and the resulting vapor and / or the gases such ¬ are fed to the exhaust stream.