Patent Application
20240026812
This application claims priority on German Patent Application No 10 2022 118 325.4 filed Jul. 21, 2022, the entire disclosure of which is incorporated herein by reference.
The invention relates to an electric exhaust turbocharger having a turbine wheel, a compressor wheel that is non-rotatably connected to and driven by the turbine wheel, and a drive engine that can be connected as needed.
U.S. Pat. No. 7,025,579 B2 discloses an electric exhaust turbocharger with an electric drive engine arranged on an end of the rotor shaft. The electric drive engine represents a flow obstacle on the suction side of the compressor wheel. Both the rotor shaft of the fluidic segment of the exhaust turbocharger and the engine shaft are supported with two bearings each. These bearings must be designed for speeds above 200,000 rpm, so that the overall bearing requirement is very high.
Accordingly, an object of the invention is to create a simply structured and fluidically efficient electric exhaust turbocharger with high bearing quality and low bearing requirements.
The invention relates to an electric exhaust turbocharger that comprises a turbine wheel, a compressor wheel that is non-rotatably connected to the turbine wheel, and an electric drive engine axially arranged between the turbine wheel and the compressor wheel. The electric drive engine includes an engine stator and an engine rotor. The engine rotor is fixed non-rotatably to a rotor shaft, and is connected non-rotatably to the turbine wheel and to the compressor wheel via the rotor shaft. The engine rotor, the turbine wheel, the compressor wheel and the rotor shaft thus form a single rotor.
The engine rotor is axially arranged between the turbine wheel and the compressor wheel on the rotor shaft. The engine rotor preferably is arranged axially so that it is approximately centered between the two roller bearings. The axial bearing arrangement of the entire rotor is accomplished by a first roller bearing between the engine rotor and the turbine wheel, and a second roller bearing between the engine rotor and the compressor wheel.
A separate shaft mounting cassette is provided with a cassette frame that supports the two roller bearings. The engine rotor therefore is arranged in the axial center of the cassette frame so that imbalances of the engine rotor are supported symmetrically by the roller bearings. Moreover, the overall structure of the rotor, including the turbine wheel and the compressor wheel, is largely symmetric. Thus, the entire rotor can be supported with only two roller bearings. Moreover, separately manufactured cassette frame, in particular regarding the rotational bearing support of the rotor, the tolerance chains are kept short, which has a positive effect on wear, fluid sealing and manufacturing costs.
The engine rotor is preferably permanently magnetic, thereby realizing a brushless drive engine that is commutated electronically. The cassette frame preferably is made of a non-ferromagnetic material, such as aluminum or another non-magnetic metal alloy or a ceramic. This has the advantage that a non-ferromagnetic cassette frame material can reduce a distance between the drive engine and the bearings. Accordingly, it is possible to mount a longer rotor of the drive engine in the same installation space to increase performance or reduce the installation space requirement. The cassette frame surrounds the engine rotor. Thus, the non-ferromagnetic cassette frame ensures that the electromagnetic interaction between the engine rotor and the engine stator is affected only by the cassette frame to a very low degree or not at all.
The cassette frame of some embodiments comprises two end bearing segments, each supporting a roller bearing, and an engine segment with a grid structure is provided between the two bearing segments in the area of the engine rotor. The grid structure provides a rigid connection of the two, preferably largely cylindrical, bearing segments and allows for electromagnetic coupling of the engine stator and engine rotor with the least possible resistance and loss. The grid structure may define a substantially cylindrical envelope.
The grid structure of some embodiments is formed in the cassette frame engine segment by substantially axially extending grid bars. The grid bars preferably are aligned precisely in the axial direction.
The number of grid bars extending between the two bearing segments preferably corresponds to the number of stator poles defined by the engine stator. The engine stator of some embodiments has engine coil supporting stator bodies forming a plurality of pole shoes. The pole shoes form the magnetic stator poles and are circumferentially arranged between the grid bars and in the cylinder plane of the grid bars. Accordingly, one pole shoe is arranged between every two grid bars. In this way, the pole shoes can be positioned radially very close to the engine rotor, so that the electromagnetic losses caused by the cylindrical air gap between the engine stator and the engine rotor are kept low.
The cassette frame of some embodiments is constructed in two sections, and is formed by a one-piece main frame section and a one-piece end frame section. The main frame section forms a first bearing segment and the grid structure. The end frame section forms the second bearing segment.
The inner shell and/or the outer shell of at least one roller bearing may be formed directly from the rotor shaft or directly from the cassette frame, thereby reducing the number of components and shortening the tolerance chain.
A separate charger housing that directly supports the engine stator and the shaft bearing cassette is provided in some embodiments. The charger housing is not necessarily fully closed, but shields the engine stator, the engine rotor and the two roller bearings towards the outside in an approximately gas-tight manner.
The invention is explained in further detail in the following with reference to the drawings.
The exhaust turbocharger rotor 41 rotates about a rotor axial A and has of a rotor shaft 52 on which a permanently magnetic engine rotor 54 is axially arranged and approximately centered with the turbine wheel 12 on the drive side and the compressor wheel 14 on the compressor side. All of the aforementioned segments of the exhaust turbocharger rotor 41 are non-rotatably connected to each other.
The rotor shaft 52 is part of a shaft bearing cassette 40 having a two-piece cassette frame 71 that supports two roller bearings 60, 60′. A first roller bearing 60 is arranged axially between turbine wheel 12 and the engine rotor 54, and a second roller bearing 60′ is axially arranged between the engine rotor 54 and the compressor wheel 14. The two-piece cassette frame 71 has two end bearing segments 70, 74, and each supports one of the roller bearings 60, 60′. An engine segment 72 is between the two end bearing segments 70, 74 and has a grid structure in the form of precisely axially oriented grid bars 46 rigidly connecting the two bearing segments 70, 74. The cassette frame 71 is made of a non-ferromagnetic metal, such as aluminum.
The drive engine includes an annular engine stator 30 that essentially comprises a punch-packed stator body 34 and engine coils 32 supported by the stator body 34. The stator body 34 forms pole shoes 34′ that form the electromagnetic stator poles and, when viewed circumferentially, are arranged in the spaces between the grid bars 46. The number of pole shoes 34′ therefore corresponds exactly to the number of grid bars 46. In this way, the pole shoes 34′ protrude radially close to the engine rotor 54 such that the electromagnetic air gap between the engine rotor 54 and the engine stator can be kept small.
The cassette frame 71 has two sections, namely, a one-piece main frame segment 42 and a one-piece end frame segment 44. The one-piece main frame segment 42 comprises a first bearing segment 70 and the grid bars 46 of the grid structure. The one-piece end frame segment 44 forms the second bearing segment 74. The cassette frame 71 has ring grooves 90′ facing radially outward at its longitudinal ends, and elastic 90 are seated in the ring grooves 90′. The cassette frame 71 is supported indirectly over the ring grooves 90′ in a separate charger housing 20.
The charger housing 20 is formed in two parts and comprises a pot-like main housing 22 and a housing cover 24. The pot-like main housing 22 encloses the first bearing segment 70 and the engine segment 72, and the housing cover 24 substantially encloses the second bearing segment 74. The main housing 22 and the housing cover 24 have a fluid-tight connection to each other via a flange connection with threaded screws 25.
The two roller bearings 60, 60′ can be integrated or formed independently. In the embodiment shown in
The two ring gaps between the shaft ends of the turbine wheel 12 and the compressor wheel 14 on the one hand and the corresponding opening edges of the shaft openings of the charger housing 20 are sealed in a fluid-tight manner by dynamic shaft seals 15 that prevent the penetration of combustion gases on the side of the compressor wheel 14 into the charger housing interior.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2022 118 325.4 | Jul 2022 | DE | national |
