DE102012111847A1 - High speed gear assembly for powertrain of motor vehicle, has drive shaft and second shaft that are indirectly supported in housing pot, and storage unit provided in housing pot for storage of third shaft - Google Patents

Abstract

The assembly (10) has a drive shaft (12) and a second shaft (14). The drive shaft is coupled with spur gear gearings (36, 38) provided with a first gear stage (39). A housing (18) is provided with a housing pot (20) and a housing cover (22). The drive shaft is indirectly supported in the housing pot. The second shaft is indirectly supported in the housing pot. The housing pot is provided with a storage unit (30) for storage of a third shaft. The housing pot is provided with a centering seat (24) for attachment of a turbine. An independent claim is also included for a powertrain of a motor vehicle.

Description

The present invention relates to a high-speed transmission assembly having a drive shaft and a second shaft coupled to the drive shaft via a spur gear forming at least a first gear stage, the high-speed gear assembly further comprising a housing having a housing pot and a Housing cover, wherein the drive shaft at least indirectly, ie directly or indirectly, is mounted in the housing pot, wherein the second shaft at least indirectly, i. directly or indirectly, is stored in the housing pot.

Such gear arrangements are well known in the art.

In motor vehicles of modern design, the energy balance of the entire drive system acquires more and more importance. It has been found that, for example, in conventional motor vehicles, which work with an internal combustion engine, about 30% of the energy provided in the form of fuel escape from the system via the exhaust gas of the internal combustion engine. A first starting point for improving the overall energy balance is thus a use of the waste heat of the internal combustion engine.

Consequently, in the prior art propulsion systems have been proposed in which the waste heat of the internal combustion engine is used to vaporize a fluid in a separate circuit. The resulting steam is then fed to a turbine and relaxed in this, so that mechanical energy is available on an output shaft of the turbine. Such a turbine has a high speed, which then has to be lowered via a transmission to a speed level that has certain output-side requirements to meet. On the output side, for example, the internal combustion engine itself be connected via the crankshaft, or it can, for example, an electric machine that is operated as a generator, be provided for converting the mechanical energy into electrical energy, wherein the electrical energy can be used in the motor vehicle.

Systems there are used for internal combustion engines to reduce fuel consumption and CO ₂ emissions. Such systems are not yet available in the market in large volumes, so that the necessary components for speed conversion are used individually connected in series. The turbine, a first gear stage, a clutch and a second gear stage are each in their own separate unit, which are installed one behind the other. A combination of these individual elements then leads to a system that has a high space requirement and is also associated with high costs.

In the 1 schematically such a sequence of elements is shown. In a turbine 2 a fluid heated by the exhaust gas is released, and the energy on the output shaft of the turbine 2 is present with a relatively high speed and a small moment. The speed is achieved by means of a first gear stage 3 reduced, after the first gear stage 3 is a clutch 4 provided that the first gear stage 3 with a second gear stage 5 coupled. From the second gear stage 5 then becomes an output unit 6 driven, which may be, for example, turn the crankshaft, for example, the internal combustion engine or an electric machine. By means of the coupling 4 can the power transmission between the first gear stage 3 and the second gear stage 5 optionally interrupted and the turbine 2 from the output unit 6 be decoupled.

The combination of the individual aggregates 2 . 3 . 4 . 5 and 6 However, leads to high system costs and a high space requirement. An object of the present invention is therefore to eliminate the above-mentioned disadvantages and to provide a gear assembly and a drive train in which the system costs are reduced and less space is required.

According to the invention, it is therefore proposed to further develop the transmission arrangement mentioned at the outset in such a way that the housing pot furthermore has a bearing receptacle for mounting a third shaft.

In this way, a basis is laid for a gear arrangement on a drive unit, which is adapted for different ratios to different output units, such as an electric machine or a mechanical output unit, such as internal combustion engine, a compressor or a fluid pump. The gear ratios and their respective pinions and wheels can be surrounded by a gear housing that is formed from the housing pot and the housing cover. In particular, the transmission housing can only consist of the housing pot and the housing cover. In addition to a compact and inexpensive construction in this way a modularity is provided, which can further contribute to a cost reduction. By means of the proposed structure, it is possible to form the gear arrangement either as a single-stage or as a multi-stage, in particular two-stage, spur gear, which is designed for high speeds. For example, a conversion from a drive speed of about 80,000 RPM or even 150,000 RPM to an output speed of about 1,800 rpm. By a high degree of integration of the interfaces for prime mover, shafts and clutch a cost-effective compact unit can be provided.

The housing provided has, according to the invention, a "housing cover" and a "housing pot". It thus consists of two elements which are connected to each other and absorb the other components of the gear assembly in itself. The terms "housing cover" and "housing pot" are not to be understood as limiting the geometric design of the housing cover or the housing pot. In particular, both the housing pot and the housing cover can substantially have a pot-like configuration and encompass, for example, more or less half of the enclosed volume.

A "bearing receptacle" is understood to mean a corresponding design of the housing pot or of the housing cover, which makes it possible to accommodate at least one part of a bearing for a shaft. For example, the housing pot or the housing cover has a circular recess into which the outer ring of a roller bearing can be introduced. In principle, it is of course also possible that the housing pot or the housing cover itself is processed in such a way that it already acts as part of a bearing.

The spur gear toothing, which couples the drive shaft to the second shaft, is "at least one stage". It can therefore be done only a single-stage translation of the drive shaft to the second shaft. However, it can also be provided that the coupling of the drive shaft to the second shaft is multi-stage, in particular two-stage design. Is yet another translation stage of the second wave to a third wave, which forms an output shaft, provided, then, for example, results in a total of three-stage construction. This can be used, for example, to translate an input speed of about 150,000 1 / min to an output speed of about 1,800 1 / min. A ratio of the drive shaft to the second shaft or countershaft is preferably greater than 6, to keep ventilation losses of the high-speed transmission assembly small, in particular none than 10%.

A "high-speed transmission arrangement" according to the present invention is characterized in particular by the configuration of the structure of the spur gear toothing, which provides the at least single-stage transmission from the drive shaft to the second shaft. On the one hand, the ratio of the drive shaft to the second shaft is greater than 6, in particular greater than 8, in particular greater than 10. On the other hand, the modulus of the teeth is selected to be small, preferably less than or equal to 1, in particular less than or equal to 1.5, in particular less than or equal to 2.0, in particular less than or equal to 2.5. In this way, in particular the ventilation losses of a high-speed transmission arrangement can be further minimized, preferably to less than 10% of the input power. The modulus is defined in the usual way as a gearing dimension, namely as the quotient of pitch circle diameter d (in mm) and tooth number z, or pitch p and circle number π: Another influencing factor of the gear geometry on the ventilation losses may be the tooth width, which is preferably selected as narrow as possible in high-speed gearboxes. Ultimately, the number of teeth ratio, so the ratio of large wheel to small wheel of a gear pairing to choose as small as possible.

According to a further aspect of the invention, it is proposed to provide a drive train for a motor vehicle, wherein the drive train comprises an internal combustion engine and a turbine, wherein the turbine is provided for the recovery of energy from an exhaust gas of the internal combustion engine. Furthermore, the drive train has an output unit, which in turn may, for example, be the internal combustion engine or else an electric machine. The powertrain is characterized by a transmission assembly or one of its configurations as mentioned above, wherein the transmission assembly is provided to couple the turbine to the power take off assembly.

The proposed powertrain thus provides the same advantages as the transmission assembly according to the first aspect of the invention.

The object initially posed is thus completely solved.

In one embodiment of the transmission arrangement can be provided that the second shaft forms an output shaft of the transmission assembly, wherein a rotation axis of the drive shaft and a rotation axis of the output shaft are different from each other. In particular, this embodiment together with the preamble of claim 1 form an independent and separate invention, which can be implemented independently of the features of the characterizing part of claim 1. Furthermore, this independent invention can be combined with the features of the remaining embodiments.

In this way it becomes possible by means of the proposed gear arrangements To provide single-stage helical gear. Such a gear arrangement can build short in the axial direction, that is, in the longitudinal axis of the direction of the drive shaft and the second shaft.

In a further embodiment of the gear arrangement can be provided that the second shaft is a countershaft of the gear assembly, wherein the gear assembly comprises a third shaft which forms an output shaft of the gear assembly, wherein the third shaft is coupled via a further spur gear toothing with the countershaft.

In this way, a two-stage gear arrangement can be provided. In particular, to provide the two-stage gear assembly, it is not necessary to use a new housing pot. It can be used the same housing pot as in the single-stage variant. Only the housing cover is to be exchanged. The two-stage gear arrangement in which the first stage is provided by means of the spur gear teeth between the drive shaft and countershaft and the second gear stage by the spur gear between countershaft and output shaft, a speed can also be further reduced.

In one embodiment of the gear arrangement can be provided that a rotation axis of the drive shaft and a rotation axis of the output shaft are different from each other.

In particular, in the two-stage gear arrangement in which the third shaft forms the output shaft, it can thus be provided that the drive and the output shaft are not coaxial to each other, but the axis of rotation in the drive and the output shaft offset from each other. In this way, further axial space can be saved.

In one embodiment of the gear arrangement can be provided that the housing pot has a centering seat for mounting a turbine.

In particular, it can be provided that the turbine can be flanged directly to the housing pot. The housing pot thus has a flange with a centering, with which the turbine can be screwed directly to the gear assembly. A drive gear of the first gear stage can be arranged directly on the turbine shaft. The drive pinion of the first gear stage may even be formed integrally with the turbine shaft. The turbine shaft can thus form the drive shaft of the transmission assembly.

In a further embodiment of the gear arrangement is provided that the second shaft is mounted in the housing cover. The second wave is stored both in their capacity as output shaft in the case of a single-stage training as well as in their capacity as a countershaft in the case of a two-stage design in the housing pot and in the housing cover.

In the housing pot thus one side of the second shaft, the drive shaft and optionally mounted in the two-stage embodiment, one side of the third shaft. However, a bearing receptacle for the corresponding bearing of the third shaft is present in the housing pot in any case.

In a further embodiment of the gear arrangement can be provided that the countershaft is mounted in the housing cover and the output shaft is mounted in the housing cover.

The housing cover thus accommodates both the countershaft and the drive shaft in the two-stage design of the gear assembly.

In a further embodiment of the transmission arrangement, it can be provided that a clutch is provided between a driven gear forming an output side of the first gear stage and the second shaft.

In particular, the clutch is formed switchable. The coupling is used for torsional vibration isolation between the turbine and an internal combustion engine, if the internal combustion engine is coupled as an output unit with the output shaft, for example via a camshaft or crankshaft. Furthermore, the clutch serves for the possibility of switching off the turbine during a cold start and a shutdown of the internal combustion engine.

In one embodiment, the coupling is designed as a fluid coupling.

Such fluid couplings in the form of hydraulic couplings are basically known to the average person skilled in the art. Between a first coupling part and a second coupling part is a cavity which can be filled by a pressurized fluid. By means of kinetic energy, a transferring connection between the first and the second part is provided via the fluid, so that the first part or the drive-side part and the second part or the output-side part of the fluid coupling are dragged along. In particular, the drive-side part of the fluid coupling is integrated in the output gear of the first gear stage. This means that it is either with the output gear of the first gear stage is rotatably connected or even integrally formed with this.

The switching of the fluid coupling takes place via a filling control of the fluid coupling with the corresponding gear oil of the gear arrangement. The transmission oil can be introduced via the hollow countershaft centrally from the inside into the fluid coupling. As heat dissipation from the fluid coupling, the oil flows at an outer diameter of the fluid coupling via throttle bores again. To switch off or open the fluid coupling, the oil flow is interrupted by a hydraulic valve.

In one embodiment of the transmission arrangement can be provided that the fluid coupling comprises a drive coupling element and an output coupling element, wherein the output coupling element is rotatably coupled to the second shaft, and wherein the drive coupling member rotatably connected to the output gear or is integrally formed with the output gear.

As already stated above, in this way a particularly compact construction of the gear arrangement is provided both in the single-stage and in the two-stage configuration.

In a further embodiment of the gear arrangement can be provided that the second shaft is hollow and a fluid supply of a fluid coupling is formed, which is arranged between an output side of the first gear stage forming output gear and the second shaft. In particular, this embodiment together with the preamble of claim 1 form an independent and separate invention, which can be implemented independently of the features of the characterizing part of claim 1. Furthermore, this independent invention can be combined with the features of the remaining embodiments.

As already stated above, can be provided in this way, particularly space-saving, the supply of a fluid of the fluid coupling. A supply or injection and a hydraulic valve can be mounted in the housing cover.

In a further embodiment of the gear arrangement can be provided that the housing cover has a centering seat for attaching an electrical machine. In particular, this embodiment together with the preamble of claim 1 form an independent and separate invention, which can be implemented independently of the features of the characterizing part of claim 1. Furthermore, this independent invention can be combined with the features of the remaining embodiments.

Similar to the integration of the turbines on the housing pot, a direct attachment of an electrical machine on the drive side can thus be provided in an axially short design.

In a further embodiment of the gear arrangement can be provided that the gear assembly further comprises an electric machine, wherein the electric machine has a stator which is arranged in the housing cover, and wherein a first end of the output shaft is mounted at least indirectly in the housing pot and a first end opposite the second end of the output shaft is designed as a rotor of the electric machine.

In this way, a further integration of the individual components is achieved to an overall system. The electric machine is thus integrated directly in the housing cover. In particular, the output shaft of the gear assembly is used at the same time as the rotor of the electric machine. The first end of the output shaft is "at least indirectly" mounted on the housing pot. In the case of the two-stage design of the gear assembly, it is mounted directly in the bearing provided for the third shaft bearing receptacle of the housing pot. If the gear arrangement is designed in one stage, so that the second shaft forms the output shaft and the output unit is of a mechanical nature, the clutch is furthermore provided. Then, the output shaft may be mounted indirectly in the housing pot by the output shaft is rotatably mounted in a hollow shaft, which in turn is mounted in the housing pot. On the hollow shaft, for example, the output gear of the first gear stage can be mounted rotatably. The output unit of a mechanical type may in all embodiments of the invention be an internal combustion engine, a compressor or a fluid pump drive. The compressor or the fluid pump drive can be arranged for example in an air conditioning or compressed air circuit, for example in a motor vehicle.

For modularization, the housing cover can, as already stated above, be equipped with a flange in a centering seat, to which an electrical machine can be connected in order thus to generate electrical current as a form of the output energy. By integrating the stator and rotor directly in the housing cover, the costs of the entire system can be further reduced.

In order for the different drive variants, that is electrical machine or internal combustion engine, as many identical parts are present, the external oil supply and oil discharge connections are preferably arranged in the housing pot. Likewise, preferably in the housing pot, the oil distribution and oil supply to the injection line for the lubrication of the teeth and arranged in front of the pressure filter. Preferably, the bearings of the gear assembly are arranged to the combustion engine to the housing pot.

In the housing cover can then be arranged in embodiments, all elements for actuating the fluid coupling such as hydraulic valve and oil supply in the hollow countershaft. Since with a mechanical output, e.g. Drive the internal combustion engine, the fluid coupling is required and not at an output to an electric machine, thus does not need to be changed by this division of the arrangement of the components of the housing pot.

Alternatively, it is also possible to arrange the elements for actuating the fluid coupling such as hydraulic valve and oil supply in the hollow countershaft in the housing pot. The oil supply to the fluid coupling via the housing pot-side end of the countershaft or second shaft. It can therefore be provided that all oil supply and oil discharge connections or fluid supply and fluid discharge connections are arranged in the housing pot. This can simplify the construction of the housing cover and improve the modularity of the gear assembly.

By means of the described arrangement of components, a modular gear arrangement for fulfilling the functions in the application of the loss energy recovery of the internal combustion engine can be implemented cost-effectively.

In a further embodiment of the gear arrangement, lubrication of the gear arrangement is designed as dry sump lubrication. This also helps to keep the losses, in particular the ventilation losses, low within the gear arrangement.

In a further embodiment of the drive train can be provided that an output shaft of the turbine is the drive shaft of the transmission assembly.

In this way, a further compact design of the drive train is made possible. In particular, a drive pinion of the first gear stage either rotatably connected to the output shaft of the turbine or even be formed integrally therewith.

It is understood that the features mentioned above and those yet to be explained below can be used not only in the particular combination given, but also in other combinations or in isolation, without departing from the scope of the present invention.

Embodiments of the invention are illustrated in the drawings and will be explained in more detail in the following description. Show it:

1 a schematic representation of a drive train according to the prior art;

2 a first embodiment of a high-speed transmission assembly according to the invention in a single-stage design and mechanical output;

3 a further embodiment of the high-speed transmission assembly according to the invention with single-stage arrangement with electric drive;

4 a further embodiment of a high-speed transmission assembly according to the invention in two-stage design with mechanical output;

5 a further embodiment of a high-speed transmission assembly according to the invention in two-stage design with electric drive;

6 a detailed representation of a high-speed transmission assembly with associated oil circuit in the example of the embodiment in 4 ;

7 an isometric view of a schematic representation similar to the embodiment in 6 ;

8th an isometric view of another embodiment of a high-speed transmission assembly according to the invention in two-stage design with mechanical output;

9 an isometric view of an embodiment of a high-speed transmission assembly according to the invention in a three-stage design with mechanical output;

10 an isometric view of another embodiment of a high-speed transmission assembly according to the invention in a three-stage design with mechanical output;

11a a schematic representation of an embodiment of a drive train; and

11b a further embodiment of the drive train in combination with a mechanical output unit.

In 1 is as already described a powertrain 1 represented according to the prior art. The powertrain 1 The prior art has a turbine 2 on, by means of the waste heat of the internal combustion engine and optionally an intermediate fluid circuit in which is generated by the exhaust heat, steam is driven. Such a turbine 2 may for example have an output speed of about 80,000 1 / min. About a first gear stage 3 and a second gear stage 5 This speed is then reduced, so that a coupling to an output unit 6 which in turn may be the internal combustion engine or, for example, an electric machine. After the first gear stage 3 and before the second gear stage 5 is a clutch 4 provided to the turbine 2 from the output unit 6 to decouple. All elements are constructed axially one behind the other. Drive and output shafts are coaxial with each other, so that a relatively large axial space is needed.

In 2 is a first embodiment of a transmission arrangement 10 shown. The in the 2 illustrated embodiment of the transmission arrangement 10 is single-stage and with a clutch 40 designed. It is therefore particularly suitable for coupling with a mechanical output unit, such as an internal combustion engine, a compressor or a fluid pump.

The gear arrangement 10 has a drive shaft 12 which rotates at a speed n ₁ . Furthermore, the gear arrangement 10 a second wave 14 which rotates at a speed n ₂ which is lower than the speed n ₁ . The second wave 14 forms in the illustrated embodiment, an output shaft 16 out.

The gear arrangement 10 has a housing 18 on, that from a housing pot 20 and a housing cover 22 is formed. On the housing pot 20 is a centering seat 24 designed for flanging a turbine. At the drive shaft 12 it can be an output shaft of the turbine. The drive shaft 12 can by means of a warehouse 26 in the housing pot 20 be stored. The second wave 14 is by means of a warehouse 28 in the housing pot 20 stored. Furthermore, in the housing pot 20 a camp recording 30 provided in the in 2 illustrated embodiment, however, is not used.

An axis of rotation 13 the drive shaft 12 and a rotation axis 15 the output shaft 16 run staggered to each other. They are not identical.

In the housing cover is another camp 32 for the second wave 14 or the output shaft 16 intended. Furthermore, the housing cover 22 a centering seat 33 for flanging a mechanical output unit.

The housing cover 22 and the housing pot 20 are by means of a housing flange 34 connected with each other.

A drive pinion 36 and a driven wheel 38 mesh with each other and form a first gear stage 39 out. The drive pinion 36 and the output gear 38 are front-toothed. This may be any suitable toothing, for example a straight toothing but also a helical toothing or an arrow toothing or the like.

The driven wheel 38 is about a clutch 40 with the second wave 14 or the output shaft 16 switchable coupled. In this way it is optionally possible, a power transmission from the drive shaft 12 on the output shaft 16 to switch. In particular, it is the coupling 40 around a fluid coupling. In this way it is possible the drive shaft 12 mechanically from the output shaft 16 to decouple and mechanically decouple in this way a drive side arranged turbine with a driven side arranged mechanical output unit.

By means of the proposed solution, it is possible to provide the turbine, gear stage, clutch and possibly output unit integrated with little space to each other.

3 shows a further embodiment of the transmission arrangement 10 , In the in 3 illustrated embodiment is the gear assembly 10 designed in one stage and has as output unit one in the housing cover 22 integrated electric machine 42 on.

Same elements are in the 3 denoted by the same reference numerals and will not be explained again below. It only goes into the differences.

In particular, the housing pot 20 like the one in the 2 illustrated housing pot 20 educated. Only one to the modified output unit adapted housing cover 22 must be provided.

In the first gear stage 39 is not a clutch in the case of an electric power take off unit 40 provided. Consequently, the driven wheel 38 with a first end 110 in the warehouse 28 in the housing pot 20 stored. Furthermore, it is in the warehouse 32 in the housing cover 22 stored. A first end 110 opposite second end 112 the second wave 14 forms a rotor 44 the electric machine 42 out. The electric machine 42 forms the output unit. By means of the electric machine 42 , which is operated as a generator, it is thus possible to convert the mechanical energy into electrical energy. A stator 46 the electric machine 42 is in a stator holder 48 arranged in the housing cover 22 is formed and in particular integral with the housing cover 22 can be. It can be provided that the housing receptacle 48 with a closure element 50 , For example, in the form of a bearing cap, is closable. It is alternatively or additionally possible that the rotor 44 also in the housing cover 22 , for example in the warehouse 32 , and / or in the closure element 50 is stored.

In this way, a single-stage gear arrangement can thus be provided in a compact design, in which the electric machine forming the output element 42 directly into the housing cover 22 is integrated.

4 shows a further embodiment of the transmission arrangement 10 , Identical elements are identified by the same reference numerals and will therefore not be explained again. The in the 4 illustrated gear arrangement 10 is designed as a two-stage gear arrangement.

For this purpose, the gear assembly 10 a third wave 52 on. The third wave 52 is in the warehouse 30 of the housing pot 20 stored. The camp recording 30 thus finds only in the two-stage embodiment of the transmission assembly 10 Use. Furthermore, the third wave 52 in a warehouse 54 in the housing cover 22 stored. The third wave 52 forms the output shaft 16 out.

The second wave 14 forms in the two-stage embodiment of the transmission assembly 10 a countershaft 56 out. The rotation axis 13 the drive shaft 12 , the rotation axis 15 the countershaft 56 and a rotation axis 53 the third wave 52 , or the output shaft 16 are not arranged coaxially with each other, but different from each other or offset. In this way, a compact axial design is possible. A second gear stage 62 is by means of one with the countershaft 56 rotatably connected drive pinion 58 provided. Of course, the drive pinion 58 the second gear stage 62 also in one piece with the countershaft 56 be educated. The same applies to a driven wheel 60 the second gear stage 62 , the rotation with the third wave 52 may be connected or integrally formed with this. The drive pinion 58 and the output gear 60 the second gear stage 62 are each spur gears and mesh with each other. The toothing can be designed in a suitable manner. For example, a straight toothing or a helical toothing or an arrow toothing can be selected.

The driven wheel 38 the first gear stage 39 is by means of a clutch 40 with the second wave 14 or the counter-wave 56 coupled. Basically, any suitable coupling 40 that is switchable, be chosen. In particular, the clutch 40 however, a fluid coupling. In this way, when using the in the 4 illustrated embodiment of the transmission arrangement 10 together with a mechanical output unit by means of the coupling 40 the power flow can be selectively interrupted and in this way a vibration-technical decoupling between a drive side arranged turbine and a driven side arranged mechanical driven unit can be provided.

By means of in 4 illustrated embodiment is a compact two-stage gear assembly 10 which can also provide large translations. For example, on the drive side, a speed of about 80,000 1 / min on the drive shaft 12 be provided. Output side on the output shaft 16 can be provided about 1,800 1 / min. For this purpose, both the first and the second gear stage has a transmission ratio of 4 to 8 respectively. In particular, the first gear stage, in particular the first gear stage 39 , have a ratio of more than 6, to keep ventilation losses low.

In the 5 is another embodiment of the transmission assembly 10 shown. The in the 5 illustrated embodiment shows a two-stage gear assembly 10 together with an electric machine 42 as output unit. Identical elements are identified by the same reference numerals and will therefore not be explained again. In the following, only the differences are discussed.

In the illustrated embodiment, the electric machine 42 similar to the illustration in 3 directly into the housing cover 22 implemented. The housing pot 20 can be identical to the representations of 2 . 3 and 4 educated be what the modularity of the entire gear assembly 10 favors and thus lowers costs.

The warehouse 54 in the housing cover 22 serves for the output side mounting of the third shaft 52 , The third wave 52 as output shaft 16 is with the first end 110 in the warehouse 30 of the housing pot 20 stored. The opposite end 112 forms the rotor 44 the electric machine 42 out. In this way it is possible, even with an electric machine 42 as output unit and modifications to the housing cover 22 the gear arrangement 10 to train in two stages. The entire housing pot 20 and the drive-side bearings can be identical, for example as in the 3 , to be kept. It is alternatively or additionally possible that the rotor 44 also in the housing cover 22 , for example in the warehouse 54 , and / or in the closure element 50 is stored.

In the 6 is in the 4 illustrated schematic embodiment of the transmission arrangement 10 in two-stage version with for a mechanical output unit with further details shown. Like elements are identified by like reference numerals and will not be explained again.

The fluid coupling 64 has a drive coupling element 66 and an output coupling element 68 on. The drive coupling element 66 is non-rotatable with the output gear 38 the first gear stage 39 connected, or may be integrally configured with this. The driven wheel 38 and the drive coupling element 66 are in a clutch bearing 70 on the output coupling element 68 or the second wave 14 supported. Furthermore, the drive coupling element 66 or output gear 38 the first gear stage 39 in the housing pot 20 by means of the warehouse 28 supported. The output coupling element 68 is non-rotatable with the second shaft 14 formed or integrally formed with this. The second wave 14 is in the warehouse 32 in the housing cover 22 supported. The second wave 14 is hollow. About the hollow second wave 14 can be a gear oil as fluid for the fluid coupling 64 from the inside radially into the space between the drive coupling element 66 and the output coupling element 68 inflow and couple these forces. Radially outward, the transmission oil flows out again warmed up and enters the interior of the housing 18 one, where there are the remaining gears of the first gear stage 39 and the second gear stage 62 as well as the bearings 26 . 30 . 28 . 32 and 54 can lubricate. A hydraulic valve 86 can the inflow of the fluid into the fluid coupling 64 control and switch with it.

It can be provided that as in the 6 and also in the 7 shown the supply of the fluid through the hollow second shaft 56 he follows. In this case, the supply line is through the housing cover 22 , Alternatively, however, as in the embodiments of the 8th . 9 and 10 is shown, a feed line through a shaft portion 57 that the output gear 38 carries. In this case, it becomes possible to supply all the supply lines for the transmission oil or the fluid in the housing pot 20 to arrange. This simplifies the construction of a housing cover 22 and thereby facilitates the modular design of the overall concept.

Lubrication of the gearbox assembly 10 is in the case 18 designed as a dry sump.

These flows over one or more outlets 74 the oil from the case 18 to the outside, goes through an oil cooler 76 and an oil filter 78 and flows back into a tank 80 , From the tank 80 it is done by means of a pump 82 that of a motor 84 is driven, pumped into the circulation. There it first passes over a first branch to the hydraulic valve 86 for selectively switching the fluid coupling 64 , Through the line 72 and in the following an orifice 88 the oil can optionally one in the housing pot 20 arranged pressure filter 90 be supplied, this flow and from this in injection nozzles 92 also in the housing pot 20 are arranged, the transmission oil also to various locations in the interior of the housing 18 to lead. In particular, it may further be provided that the orifice plate 88 in the housing pot 20 is arranged.

Next to the pump 82 and the tank 80 In principle, it can also be provided as an alternative that the gear arrangement 10 the gear oil is obtained from an internal combustion engine, or embedded in the oil circuit. Such a configuration may be a separate pump 82 with engine 84 for the gear arrangement 10 save on. Furthermore, it can be provided that the pump 82 in the housing pot 20 is arranged. Also the tank 80 can in the housing pot 20 be educated. A drive of the pump 82 can then by means of a separate engine 84 , in particular an electric motor, take place. It is also possible that the pump 82 with either the second wave 14 , but preferably with the third wave 16 is coupled and thus mechanically driven via this.

In the 7 FIG. 3 is a schematic isometric view of an embodiment similar to the embodiment of FIG 6 shown. Identical elements are identified by the same reference numerals and will therefore not be explained again.

In particular, the second wave can be seen 14 holding a hollow interior 94 , in particular in the form of a bore, which has an oil feed into the fluid coupling 64 forms. An inlet opening 96 is located for this purpose in the housing cover 22 so directly on it the valve 86 can be applied. You can also see another camp 98 , by means of which the second wave 14 or counter-wave 56 together with the warehouse 70 . 28 and 32 in the housing cover 22 and housing pot 20 is supported. In this case, therefore, the second wave 14 or counter-wave 56 directly over the camp 32 in the housing cover 22 supported and further indirectly via the clutch bearing 70 , which may for example be designed as a needle bearing or sliding bearing, via the output gear 38 and the camp 28 in the housing pot 20 supported.

The 8th shows an isometric view of another embodiment, which is basically similar to the embodiment in 7 is trained. The same elements are therefore identified by the same reference numerals and will therefore not be explained again.

One difference is that the second wave 14 in the direction of the housing pot 20 is hollow. In this way, a fluid supply into the fluid coupling 64 in the housing pot 20 be educated. This allows all fluid feeds and drains in the housing pot 20 to arrange, in particular all the above-mentioned fluid supplies and drains.

The 9 shows a three-stage embodiment of a high-speed transmission assembly 10 , Identical elements are identified by the same reference numerals and will therefore not be explained again.

In contrast to the single-stage and two-stage embodiments is in the in 9 illustrated gear arrangement 10 the translation of the drive shaft 12 on the second wave 14 already formed in two stages. Such an arrangement can serve, in particular, very high rotational speeds on the drive shaft 12 from about 150,000 RPM to about 14,000 RPM on the second wave 14 decrease. The translation to, for example, about 1,800 1 / min on the output shaft 16 can then be done in the manner described so far.

For the translation of the drive shaft 12 on the second wave 14 is an intermediate wave 114 intended. An idler 115 the intermediate shaft 114 meshes with the drive pinion 36 , An intermediate pinion 116 then meshes with the output gear 38 , In this way, an additional translation level 119 and thus achieved a total of three-stage construction. A fluid supply to the fluid coupling 64 like in the 9 shown through the housing pot 20 respectively. But it can also be a feeder as in the 6 schematically represented by the housing cover 22 respectively.

The 10 shows another three-stage embodiment of a high-speed transmission assembly 10 , Identical elements are identified by the same reference numerals and will therefore not be explained again.

As stated above, embodiments of the invention may be implemented without the characterizing feature of claim 1, after which the bearing 30 in the housing pot 20 is included. Basically, also a carrier plate 120 be provided at the camp 30 can be supported. Such an arrangement can more space for the bearings 117 and 118 the intermediate shaft 114 provide. In particular, such an arrangement can thus be used together with a mechanical output application, the fluid coupling 64 requires.

The 11a and 11b show schematically embodiments of a drive train 100 , The powertrain 100 has a turbine 104 , a gearbox arrangement 10 as for example in an embodiment according to one of 2 to 10 on. The 8A shows the electric machine 42 as output unit. The 8b shows a combustion engine 102 as output unit. But it can also be another mechanical output unit such as a compressor or a fluid pump.

In the 11a serves an internal combustion engine 102 for driving the motor vehicle. Part of the heat of the exhaust gas of the internal combustion engine 102 is used in a cycle 103 to vaporize a fluid, the steam in turn to drive a turbine 104 serves. After leaving the turbines, the fluid of the circuit 103 liquefied again and re-enters the circuit. Such thermodynamic cycles are generally known to those of ordinary skill in the art.

The powertrain 100 thus indicates the driven turbine 104 in which a performance 106 is introduced. The drive shaft 12 is formed over the turbine shaft. About the gear arrangement 10 is the turbine 104 with the electric machine 42 coupled, giving an electrical output 109 provided.

In the 11b is schematically the structure of the powertrain 100 when used with a mechanical output unit, in particular the internal combustion engine 102 shown. Again, the heat of the exhaust gas of the engine 102 Driving a motor vehicle, used to get in a cycle 103 to vaporize a fluid of the circuit so as to make the turbine 104 drive with a power 106 , The turbine shaft is in turn the drive shaft 12 the gear arrangement 10 , so that a mechanical output power 108 is provided, for example, via a camshaft or crankshaft directly to the engine 102 can support. But it can also be driven, for example, a compressor or a fluid pump or other mechanical output unit.

Claims (16)

High Speed Transmission Assembly ( 10 ), with a drive shaft ( 12 ) and a second wave ( 14 ) connected to the drive shaft ( 12 ) via a spur gear toothing ( 36 . 38 ) having at least one first gear stage ( 39 ) is coupled, wherein the gear arrangement ( 10 ) a housing ( 18 ), which has a housing pot ( 20 ) and a housing cover ( 22 ), wherein the drive shaft ( 12 ) at least indirectly in the housing pot ( 20 ), wherein the second shaft ( 14 ) at least indirectly in the housing pot ( 20 ), and characterized in that the housing pot ( 20 ) furthermore a bearing receiver ( 30 ) for supporting a third wave ( 52 ) having. High-speed gear arrangement according to claim 1 or according to the preamble of claim 1, characterized in that the second shaft ( 14 ) an output shaft ( 16 ) of the gear arrangement ( 10 ), wherein an axis of rotation ( 13 ) of the drive shaft ( 12 ) and a rotation axis ( 15 . 53 ) of the output shaft ( 16 ) are different from each other. High-speed gear arrangement according to claim 1 or 2, characterized in that the second shaft ( 14 ) a countershaft ( 56 ) of the gear arrangement ( 10 ), the gear arrangement ( 10 ) a third wave ( 52 ), which has an output shaft ( 16 ) of the gear arrangement ( 10 ), the third wave ( 52 ) via a further spur gear toothing ( 58 . 60 ) with the countershaft ( 56 ) is coupled. High-speed gear arrangement according to claim 3, characterized in that a rotation axis ( 13 ) of the drive shaft ( 12 ) and a rotation axis ( 15 . 53 ) of the output shaft ( 16 ) are different from each other. High-speed gear arrangement according to one of claims 1 to 4, characterized in that the housing pot ( 20 ) a centering seat ( 24 ) for mounting a turbine ( 104 ) having. High-speed gear arrangement according to one of claims 1 to 5, characterized in that the second shaft ( 14 ) in the housing cover ( 22 ) is stored. High-speed gear arrangement according to one of claims 3 to 6, characterized in that the countershaft ( 56 ) in the housing cover ( 22 ) is mounted and the output shaft ( 16 ) in the housing cover ( 22 ) is stored. High-speed gear arrangement according to one of claims 1 to 7, characterized in that between a an output side of the first gear stage ( 39 ) forming output wheel ( 38 ) and the second wave ( 14 ) a coupling ( 40 ). High-speed gear arrangement according to claim 8, characterized in that the clutch ( 40 ) a fluid coupling ( 64 ). High-speed gear arrangement according to claim 9, characterized in that the fluid coupling ( 64 ) a drive coupling element ( 66 ) and an output coupling element ( 68 ), wherein the output coupling element ( 68 ) rotatably with the second shaft ( 14 ), and wherein the drive coupling element ( 66 ) rotatably with the output gear ( 38 ) or in one piece with the output gear ( 38 ) is trained. High-speed gear arrangement according to one of claims 1 to 10 or according to the preamble of claim 1, characterized in that the second shaft ( 14 ) is hollow and a fluid supply ( 94 ) a fluid coupling ( 64 ) formed between a an output side of the first gear stage ( 39 ) forming output wheel ( 38 ) and the second wave ( 14 ) is arranged. High-speed gear arrangement according to one of claims 1 to 11 or according to the preamble of claim 1, characterized in that the housing cover ( 22 ) a centering seat ( 33 ) for attaching an electric machine ( 42 ) having. High-speed gear arrangement according to one of claims 2 to 11, characterized in that the gear arrangement ( 10 ) further comprises an electric machine ( 42 ), wherein the electric machine ( 42 ) a stator ( 46 ), which in the housing cover ( 22 ), and wherein a first end ( 110 ) of the output shaft ( 16 ) at least indirectly in the housing pot ( 20 ) and a first end ( 110 ) opposite second end ( 112 ) of the output shaft ( 16 ) as a rotor ( 44 ) of the electric machine ( 42 ) is trained. High-speed gear arrangement according to one of claims 1 to 13, characterized in that all fluid supply and fluid discharge connections ( 74 . 86 . 92 ) in the housing pot ( 20 ) are arranged. Powertrain ( 100 ) for a motor vehicle, with an internal combustion engine ( 102 ), a turbine ( 104 ) for the recovery of energy from an exhaust gas of the internal combustion engine ( 102 ) and an output unit ( 42 . 102 ), characterized in that the output unit ( 42 . 102 ) by means of a high-speed transmission arrangement ( 10 ) according to one of claims 1 to 14 with the turbine ( 104 ) is coupled. Drive train according to claim 15, characterized in that an output shaft of the turbine ( 104 ) the drive shaft ( 12 ) of the high speed transmission assembly ( 10 ).

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