Exhaust turbochargers are a must in modern vehicles. The most important components include a turbine and a compressor. These two components are located on one and the same shaft. The exhaust of the internal combustion engine is conducted to the turbine. The exhaust powers the turbine. Then the turbine in turn powers the compressor. This takes in air from the environment and compresses it. The compressed air is then used for combustion in the engine. The purpose of exhaust turbochargers is to minimize the exhaust emissions as well as to increase the efficiency of the engine and its torque. They also have an important function in regards to the efficiency of the catalytic converter.

The following requirements are generally demanded of an exhaust turbocharger: They should fulfill the mentioned functions regarding the exhaust emission, the efficiency level and torque of the engine in the most optimal manner possible. In doing so, they should have minimal weight and minimal construction volume. The design should be simple and easy to assemble, so that manufacturing costs are held to minimal levels. They should be compatible with catalytic converters.

The known exhaust turbochargers do not fill all these functions, or only to a certain point. That is, lowering pollutant emissions during the cold start phase leaves much to be desired, and weight and space demands are unreasonably high.

The task of the invention is to design a casing aggregate of the type mentioned in such a manner that significant improvements are made in the mentioned parameters. This task is accomplished by the characteristics of Claim 1.

In accomplishing the task, the inventors stuck with the tried and true execution of the casing aggregate by casting. For this, however, they departed from the conventional method of casting steel in a sand mold, and switched to a thin-walled fine casting, also known as precision casting. This allows the wall thickness to be greatly reduced. This also greatly decreases the weight of the aggregate. The casing aggregate now has a substantially lower mass, so that only relativey small heat energy can be removed from the exhaust in the cold start phase. Thus the thermal inertia is very minimal.

As an additional measure, the casing aggregate is assembled from at least two parts. Therefore, the casing aggregate has at least one separation joint. The separation joint is arranged as follows: -it extends in an axially perpendicular level, -it runs along the apex line of the spiral casing, -it extends over an arc of a circle of approximately 270 degrees, and -it lies outside of the area of the tongue.

Thus in any case, the spiral casing is in at least two parts.

In doing so, the division into two on the basis of the separation joint described above, occurs in such a manner that the two following benefits result: For one thing, each of the two parts of the spiral casing can be cast without requiring the use of casting cores.. The shapes of the two spiral casing parts don't require any undercutting.

In addition, the separation joint is positioned in such a manner that the area of the tongue lies outside of the separation joint. The tongue area is that area this is thermally stressed the most. When the two cast parts of the spiral casing are put together, the tongue area, therefore, consists of a single piece without separation joint, which takes into account the high thermal stress and, therefore, the high demands of rigidity in this area.

The two parts can be joined, for example, using any type of welding, for example using laser welding or micro-plasma welding.

By avoiding casting cores, positional tolerances don't need to be considered while casting. This means that the wall thickness can already be less for this reason than with the classical method of using casting cores. This already results in considerable weight reduction. A multiple-part turbine casing cast in precision casting has an average wall thickness of approximately 2 mm. This means a mass reduction of 40 to 60 W in comparison to execution in cast steel in sand. In addition, the manufacturing costs of a spiral casing based on the invention are lower than before. In general, a heat resistant cast steel for exhaust temperatures of 1050°C is considered suitable as a material.

The finish and dimensional accuracy are optimal. This leads to higher efficiency levels. The manufacturing costs will already be lower because refinishing is unnecessary.

The invention is further explained in the drawings. The following details are represented: Fig. 1 shows an exhaust turbocharger in axial section.

Fig. 2 shows an enlarged section through the spiral casing of the turbine of Fig. 1.

The turbocharger shown in Fig. 1 has the following components as its most important elements: A turbine 1 with turbine wheel 1. 1, a compressor 2 with compressor wheel 2.1, a bearing 3, and a shaft 4 on which the turbine wheel 1.1 and the compressor wheel 2.1 are seated.

The turbine casing is executed in known fashion as a spiral casing. It is made of two main parts, namely a part 1.2- herein referred to as the inner part", and a part 1.3- herein referred to as the outer part". An outer exhaust support 1.4 is a component of the outer part 1.3. This could however also be separate from the outer part 1.3.

The following is decisive: The two main parts 1.2 and 1.3 of the spiral casing of the turbine are separated along a separation joint. The separation joint runs in an axially perpendicular level. It runs along the apex line of the spiral casing.

As can be seen in Fig. 2, the separation joint extends over an angle of 270 degrees. It lies outside of the tongue area 1.5 of the spiral casing. This area is highly thermally stressed.

Fig. 2 shows part 1.3. Part 1.2 is removed.

The separation joint extends from point A to point B. The area of the tongue 1.5 remains undisturbed. This means that the spiral casing is one part in the tongue area. For the purpose of assembly, part 1.2 is seated over the area of the separation joint between point A and B on part 1.3.