DE102019210501B4 - Pulley assembly - Google Patents

Abstract

Belt pulley arrangement with a switchable belt pulley (9) which is arranged on a drive shaft (1), in particular an electric machine shaft, and can be coupled to or decoupled from the drive shaft (1) in a torque-transmitting manner via a coupling device, depending on different operating modes (MB1, MB2, GB) of the pulley arrangement, wherein in a first operating mode, in particular a first motor operating mode (MB1), the coupling device couples the drive shaft (1) to the switchable pulley (9) in such a way that when the drive shaft rotates in a first drive direction of rotation (A1) forms a load path (L1) from the drive shaft (1) in the direction of the switchable pulley (9), wherein in a second operating mode, in particular a generator mode (GB), the coupling device connects the drive shaft (1) with the switchable pulley ( 9) couples in such a way that when the drive shaft rotates in the first drive The direction of rotation (A1) forms an opposing load path (L3) from the switchable belt pulley (9) into the drive shaft (1), wherein in an additional operating mode, in particular a second motor operating mode (MB2), the coupling device removes the drive shaft (1) from the switchable belt pulley ( 9) is decoupled, so that when the drive shaft rotates in an opposite, second drive direction of rotation (A2), a load path (L5) along the drive shaft (1) is formed, with the load on the switchable pulley (9) being relieved, the clutch device having an overrunning clutch (K1 ) and a centrifugal clutch (K2) which, depending on the operating mode (MB1, MB2, GB), automatically provide a coupling or decoupling between the switchable pulley (9) and the drive shaft (1), the switchable pulley (9) is arranged with the radial interposition of the overrunning clutch (K1) on the drive shaft (1), and at least the centrifugal clutch (K2) est has a centrifugal force element (15) that can be acted upon by centrifugal force, which is adjustable between a rest position and a blocking position, and the centrifugal force element (15) in the blocking position is in engagement with a mating contour (29) of the drive shaft (1) and disengaged therefrom in the rest position is, characterized in that a non-rotatable belt pulley (11) is arranged on the drive shaft (1), that the two belt pulleys (9, 11) are axially directly adjacent to one another, and that the non-rotatable belt pulley (11) has a radially inner installation space (19) provides, in which the centrifugal element (15) of the centrifugal clutch (K2) can be positioned.

Description

The invention relates to a pulley arrangement with a switchable pulley according to the preamble of claim 1.

Conventional vehicles have a drive for ancillary units. Driven by the internal combustion engine, an electric machine and a mechanical air conditioning compressor, among other things, are supplied with power. The introduction of start-stop or hybrid systems, as well as “sailing” operation and the like, greatly reduces the running time of the internal combustion engine and thus the availability of the mechanical air conditioning compressor. If air conditioning is required, there is therefore a so-called “start-stop veto”. In this case, the internal combustion engine must run or be started, although there is no request for vehicle propulsion. Starting the engine simply because there is a need for air conditioning affects the energy balance in the vehicle as a whole. An alternative is to provide an electrically driven air conditioning compressor instead of a mechanical air conditioning compressor. However, this has significant disadvantages compared to the mechanically driven air conditioning compressor with regard to procurement costs, component weight and space requirements.

A pulley arrangement has an electric machine with an electric machine shaft on which a pulley, which can be switched via a clutch device, and a non-rotatable pulley are arranged. The switchable pulley can be drivably connected to an internal combustion engine shaft via an internal combustion engine belt drive. In addition, the non-rotatable belt pulley can be connected to an assembly shaft via an assembly belt drive. In a first motor operating mode, the electric machine drives via its electric machine shaft and the internal combustion engine belt drive in a first driving direction of rotation on the internal combustion engine. In this case, an engine start of the internal combustion engine can take place, for example, or a boost mode can take place in which the running internal combustion engine is supported with an additional electromotive torque. Alternatively, in a generator operating mode, the internal combustion engine can drive onto the electric machine in the first drive direction of rotation via its internal combustion engine shaft and the internal combustion engine belt drive. In this case, the vehicle battery connected to the electric machine can be charged and the air conditioning compressor can also be driven.

The electric machine can also operate in an additional operating mode, that is to say a second engine operating mode. In the second motor operating mode, the electric machine can drive onto the auxiliary unit via its electric machine shaft and the unit belt drive, specifically when the internal combustion engine is shut down, that is to say drive onto the auxiliary unit independently of the internal combustion engine.

The implementation of the above first motor mode, the second motor mode and the generator mode is only possible in the prior art with additional actuators that have to be controlled by an external control unit. The provision of such actuators is therefore complex in terms of control technology and requires components and installation space.

From the EP 1 454 043 B1 a variable belt drive for ancillary units is known. From the DE 197 54 872 A1 a pulley for overrunning clutches with two belts is known. From the DE 10 2013 108 839 A1 a pulley assembly is known.

From the US 2009/0 298 646 A1 a generic pulley arrangement with a switchable pulley is known. From the WO 01/77 521 A1 a device for coupling at least one auxiliary unit to a main unit is known.

The object of the invention is to provide a belt pulley arrangement with a switchable belt pulley in which, compared to the prior art, the belt pulley can be switched more easily in terms of control technology and the installation space and component requirements are reduced.

The object is achieved by the features of claim 1. Preferred developments of the invention are disclosed in the subclaims.

According to the invention, actuators that can be controlled externally by means of electronic control devices can be dispensed with. Instead of this, the clutch device for the switchable belt pulley can have an overrunning clutch and a centrifugal clutch. The overrunning clutch and the centrifugal clutch open or lock automatically in the first operating mode, in the generator operating mode of the electric machine and in an additional operating mode according to the invention, i.e. without the influence of e.g. electrical or hydraulic external energy. In this way, particularly when the internal combustion engine is at a standstill (that is, when the internal combustion engine shaft is at a standstill), the electric machine can drive the auxiliary unit, in particular a mechanical air conditioning compressor, independently of the internal combustion engine.

In the first motor operating mode, the overrunning clutch can lock in a torque-transmitting manner and the centrifugal clutch can be transmission-free. In the generator operating mode, the overrunning clutch can be transmission-free and lock the centrifugal clutch in a torque-transmitting manner. In an additional operating mode, that is to say a second motor operating mode, both the overrunning clutch and the centrifugal clutch can be transmission-free.

Against this background, in a technical implementation, the torque-transmitting locking function of the overrunning clutch can be activated in the first motor operating mode for a first driving direction of rotation of the electric machine shaft. In the first engine operating mode, the electric machine can either be used to start the engine or to perform a boost function while the internal combustion engine is running. In contrast, the transmission-free freewheeling function of the freewheel clutch can be activated when the electric machine is operating in a second driving direction of rotation that is opposite to the first driving direction of rotation.

The torque-transmitting locking function of the centrifugal clutch can be activated in the generator operating mode of the electric machine. In contrast to this, their transmission-free freewheeling function can be activated when the electric machine is operating in the opposite, second driving direction of rotation.

With the above embodiment variant, the electric machine can rotate in the second drive direction of rotation in the second motor operating mode (that is to say, drive the auxiliary unit when the internal combustion engine shaft is shut down). In the second driving direction of rotation, the freewheeling functions are activated both in the overrunning clutch and in the centrifugal clutch, that is, both clutches are free of transmission. The electric machine can therefore drive the auxiliary unit even when the internal combustion engine is shut down.

According to the invention, the switchable belt pulley is arranged on the electric machine shaft with the overrunning clutch being radially interposed. In common practice, the overrunning clutch can have an overrunning clutch on the outside and an overrunning clutch on the inside. Adjustable clamping elements are arranged between the one-way clutch inside and the one-way clutch outside. Depending on the direction of rotation of the inside and the outside, the clamping elements can be adjusted into a clamping position or into a release position due to a relative movement.

The centrifugal clutch has at least one centrifugal force element that can be acted upon by centrifugal force. The centrifugal force element can be displaced between a rest position and a blocking position when the centrifugal force acts. In the locked position to which centrifugal force is applied, the centrifugal force element can be in engagement with a mating contour of the electric machine shaft. In contrast, the centrifugal force element can be out of engagement with the mating contour of the electric machine shaft in its rest position.

According to the invention, the non-rotatable belt pulley and the switchable belt pulley are arranged axially directly adjacent to one another on the electric machine shaft in a design that is advantageous in terms of installation space. With regard to an implementation that is economical in terms of installation space, the non-rotatable belt pulley provides a radially inner installation space. The centrifugal force element of the centrifugal clutch can be positioned in the installation space of the non-rotatable belt pulley. The radially inner installation space of the non-rotatable belt pulley can be formed on the side of the non-rotatable belt pulley facing the switchable belt pulley. With regard to the largest possible installation space, this can be formed between a radially outer groove ring, a radially inner hub section and a connecting flange of the non-rotatable belt pulley. The connecting flange connects the radially inner hub section with the radially outer groove ring. With this geometry of the non-rotatable belt pulley, the mating contour that interacts with the centrifugal force element can be formed directly on the inner circumference of the grooved ring of the non-rotatable belt pulley in a space-saving manner.

In a structurally simple embodiment variant, the centrifugal clutch can have a linear guide, by means of which the centrifugal element can be linearly adjusted between its rest position and its blocking position. To implement the linear guide, the switchable belt pulley can be axially extended in one piece and made of the same material with a support ring. The support ring can be reduced in diameter compared to the switchable belt pulley and, in the assembled position, protrude nested in the installation space of the axially adjacent non-rotatable belt pulley. In the support ring of the switchable pulley, at least one radially aligned guide channel can be formed in which the centrifugal force element is guided in a radially adjustable manner.

In a structurally simple development, the guide channel formed in the support ring of the switchable pulley can be axially open on the end face. In the assembled state, the axially open end face of the guide channel can be closed directly by the connecting flange of the non-rotatable belt pulley.

In the second engine operating mode, the electric machine drives the auxiliary unit independently of the (shut down) internal combustion engine. In this case, the electrical machine rotates Shaft together with the non-rotating pulley arranged on it. In contrast, the internal combustion engine belt drive together with the switchable pulley remains shut down, so that a relative rotational movement takes place between the switchable (shut down) pulley and the rotating, non-rotatable pulley and the electric machine shaft. In this case, the support ring of the switchable belt pulley can preferably be in sliding contact with the outer circumference of the hub section and with the connecting flange of the non-rotatable belt pulley or be slightly spaced therefrom.

With regard to perfect functionality, it is preferred if the centrifugal force element is spring-pretensioned with a spring into its radially inner rest position. In this case, the centrifugal force element can be in its radially inner (spring-preloaded) rest position in contact with a radial stop formed on the switchable belt pulley. Therefore, in its radially inner rest position, the centrifugal element can be out of sliding contact with the hub portion of the rotationally fixed pulley.

A radial free space can be provided between the support ring of the switchable belt pulley and the inner circumference of the ring of grooves of the non-rotatable belt pulley. When centrifugal force is applied, the centrifugal force element can come into engagement with the counter-contour formed on the inner circumference of the ring of grooves of the non-rotatable belt pulley, using up this radial free space.

It is advantageous in terms of installation space if the spring is arranged in the radial free space between the support ring of the switchable pulley and the inner circumference of the ring of grooves of the non-rotatable pulley. The radial free space can be continuously open all the way round (that is, without interruption). In this case, the spring can preferably be an annular spring, which is stretched onto the outer circumference of the support ring of the switchable pulley and / or moves around the support ring outer circumference without interruption.

With a view to positioning the annular spring in the correct position, a circumferential spring groove, in which the annular spring is arranged, can be formed on the outer circumference of the support ring of the switchable pulley. If the centrifugal force is very high, there may be a risk that the ring spring will lift off radially outward from the outer circumference of the support ring. Against this background, a circumferential (radially inwardly open) spring groove can also be formed on the inner circumference of the ring of grooves of the rotationally fixed pulley, in which the annular spring lifting off the inner circumference of the support ring can be retracted.

Regardless of the concrete structure of the pulley arrangement set out above, a general aspect of the invention is generally directed to a switchable pulley which is arranged on a drive shaft (i.e. in particular the electric machine shaft) and can be coupled to or decoupled from the drive shaft via a coupling device in a torque-transmitting manner, depending on different modes of operation of the pulley assembly. In a first operating mode (in particular the above-mentioned first motor operating mode) the coupling device couples the drive shaft to the switchable pulley in such a way that a load path is created when the drive shaft rotates in a first drive direction of rotation L1 forms from the drive shaft in the direction of the switchable pulley. In a second operating mode (that is to say in particular the generator operating mode), the coupling device couples the drive shaft to the switchable pulley in such a way that an opposing load path is created when the drive shaft rotates in the first drive direction of rotation L3 forms from the switchable pulley into the drive shaft. In a third operating mode (that is to say in particular the second motor operating mode) the clutch device decouples the drive shaft from the switchable pulley, so that a load path is created when the drive shaft rotates in an opposite, second drive direction of rotation L5 forms without power split along the drive shaft, namely with forceful relief or decoupling of the switchable pulley from the drive shaft.

An exemplary embodiment of the invention is described below with reference to the accompanying figures.

• 1 bis 3 jeweils Ansichten einer als Blockschaltdiagramm angedeuteten Riemenscheibenanordnung in unterschiedlichen Betriebszuständen;
• 4 bis 7 in Schnittdarstellungen die Kupplungseinrichtung mit deaktivierter Fliehkraftkupplung (4 und 5) sowie mit aktivierter Fliehkraftkupplung (6 und 7); und
• 8 ein Federkraft-Drehzahl-Diagramm.

Show it:

• 1 until 3 in each case views of a pulley arrangement indicated as a block diagram in different operating states;
• 4th until 7th in sectional views the clutch device with deactivated centrifugal clutch ( 4th and 5 ) as well as with activated centrifugal clutch ( 6th and 7th ); and
• 8th a spring force-speed diagram.

In the 1 a pulley assembly includes an electric machine RSG which is connected to a vehicle battery 14 via an electrical supply line. The electric machine RSG is with an internal combustion engine BKM of a vehicle and with a mechanical air conditioning compressor forming the auxiliary unit mKK instinctively connected. An electric machine shaft 1 the electric machine RSG , an aggregate shaft 3 of the air conditioning compressor mKK as well as an internal combustion engine shaft 5 are arranged axially parallel to one another and via an internal combustion engine belt drive R _BKM and via an aggregate belt drive R _mKK connected with each other instinctively. The internal combustion engine belt drive R _BKM points in the 1 one non-rotatably on the engine shaft 5 seated pulley 7th as well as a switchable pulley 9 on that on the electric machine shaft 1 is arranged. The switchable pulley 9 is by means of a clutch device described later, depending on different operating modes MB1, MB2, GB with the electric machine shaft 1 Can be coupled or decoupled to transmit torque. The aggregate belt drive R _mKK has one on the electric machine shaft 1 arranged, non-rotatable pulley 11 as well as an aggregate-side pulley 13th on.

In the 1 is the clutch device from an overrunning clutch K1 and a centrifugal clutch K2 built up. These can be found in the 1 until 3 The illustrated operating modes MB1, GB, MB2 automatically couple or decouple so that the switching operations can be carried out without external hydraulic or electric actuators. The following are based on the 1 until 3 the operating modes MB1, GB, MB2 described in which the pulley arrangement can be operated.

In the 1 the pulley arrangement works in the first motor mode MB1, in which the electric machine RSG executes an engine start or a boost function. In the first motor operating mode MB1 is in the electric machine RSG a drive torque is generated. On the clutch device of the switchable pulley 9 there is a power split, in which this is done by the electric machine RSG generated drive torque in a load path L1 from the electric machine shaft 1 in the direction of the internal combustion engine belt drive R _BKM and into a load path L2 from the electric machine shaft 1 in the direction of the unit belt drive R _mKK is divided. The electric machine wave 1 the electric machine RSG drives with a first drive direction of rotation A1 (i.e. clockwise rotation) on the engine shaft 5 and on the aggregate shaft 3 from, which is also in the first drive direction of rotation A1 turn.

In the 2 works the pulley assembly in a generator mode GB, in which one of the internal combustion engine BKM generated drive torque in a load path L3 from the engine shaft 5 via the internal combustion engine belt drive R _BKM to the electric machine shaft 1 and on to the electric machine RSG is transmitted. In addition, there is a power split in the case of the load path L3 a load path L4 branches off from the electric machine shaft 1 via the unit belt drive R _mKK to the air conditioning compressor mKK is led. The engine shaft 5 the electric machine RSG drives with the first drive direction of rotation A1 (i.e. clockwise rotation) on the electric machine shaft 1 and on the aggregate shaft 3 from, which is also in the first drive direction of rotation A1 turn. In the GB generator operating mode, the electric machine is charged RSG connected vehicle battery 14 and at the same time a drive for the air conditioning compressor mKK .

In the 3 the pulley arrangement operates in a second motor mode MB2. In the second motor operating mode MB2, a is from the electric machine RSG generated drive torque in a load path L5 without power split from the electric machine shaft 1 in the direction of the unit belt drive R _mKK transfer. The switchable pulley 9 is switched load-free by the clutch device in the second engine operating mode MB2. In contrast to the first motor operating mode MB1 and the generator operating mode GB, the electric machine drives RSG with the opposite second drive direction of rotation A2 (i.e. left turn) on the unit belt drive R _mKK away. The second engine operating mode MB2 takes place when the internal combustion engine is shut down BKM . In this case, the air conditioning compressor mKK , regardless of the internal combustion engine BKM , from the electric machine RSG be supplied with drive power.

To implement the above three modes of operation MB1, MB2, GB is in the overrunning clutch K1 the torque-transmitting locking function is activated in the first motor operating mode MB1. In this case the load path runs L1 ( 1 ) from the electric machine RSG via the locked overrunning clutch K1 as well as in the first drive direction of rotation A1 to the internal combustion engine BKM . The transmission-free freewheel function of the freewheel clutch K1 is, however, in the second engine operating mode MB2 ( 3 ) activated, that is, when the electric machine is in operation RSG in the direction of rotation of the first drive A1 opposite second drive direction of rotation A2 .

In addition, to implement the three operating modes MB1, MB2, GB is in the centrifugal clutch K2 the torque-transmitting locking function in generator operating mode GB ( 2 ) activated. In this case the load path runs L3 ( 2 ) from the internal combustion engine BKM via the internal combustion engine belt drive R _BKM as well as via the locked centrifugal clutch K2 to the electric machine RSG while at the same time in the overrunning clutch K1 the freewheel function is activated.

The transmission-free freewheeling function of the centrifugal clutch K2 is, however, in the second engine operating mode MB2 ( 3 ) activated, that is, at Operation of the electric machine RSG in the opposite second drive direction of rotation A2 ( 3 ). The load path results in the second motor operating mode MB2 L5 , in which the electric machine RSG in the second drive direction of rotation A2 rotates so that both in the overrunning clutch K1 as well as in the centrifugal clutch K2 the freewheel function is activated in each case. In this way, in an engine-off phase (that is, when the internal combustion engine is temporarily shut down BKM ) or when the internal combustion engine is permanently shut down BKM the electric machine RSG the mechanical air conditioning compressor mKK independent of the internal combustion engine BKM drive.

The following is based on the 4th until 7th a concrete structure of the switchable pulley 9 as well as the non-rotatable pulley 11 with the two freewheel and centrifugal clutches K1 and K2 Described: Accordingly, the two switchable and non-rotating pulleys 9 , 11 axially immediately adjacent to one another on the electric machine shaft 1 arranged. A basic body 12th the switchable pulley 9 is under the radial interposition of the overrunning clutch K1 on the electric machine shaft 1 arranged. As from the 4th and 5 shows the centrifugal clutch K2 A total of three centrifugal force elements that can be subjected to centrifugal force distributed evenly around the circumference 15th on that between one in the 4th and 5 shown rest position and one in the 6th and 7th locked position shown are adjustable. The basic body 12th the switchable pulley 9 is in the 4th with a diameter-reduced support ring 17th made of the same material and extended in one piece. The support ring 17th the switchable pulley 9 protrudes into an installation space 19th the non-rotating pulley 11 a. In the 1 is the installation space 19th between a radially outer ring of grooves 21 , a radially inner hub portion 23 and a connecting flange 25th the non-rotating pulley 11 arranged that the hub portion 23 with the radially outer ring of grooves 21 connects.

In the 5 is each of the centrifugal elements 15th in a radially aligned guide channel 27 guided radially adjustable. The respective guide channel 27 is in the support ring 17th the switchable pulley 9 axially open at the front. In the, in the 4th The assembly state shown is the axially open end face of the respective guide channel 27 from the connecting flange 25th the non-rotating pulley 11 closed, so that a reliable linear guide of the centrifugal force elements 15th is guaranteed.

According to the 5 is on the inner circumference of the ring of grooves 21 the non-rotating pulley 11 a counter contour 29 educated. When subjected to centrifugal force, this acts with a (in the 5 Form-fitting contour indicated by dashed lines 16 of the respectively assigned centrifugal force element 15th together. In the in the 5 The rest position shown is between the support ring 17th the switchable pulley 9 and the inner circumference of the ring of grooves 21 the non-rotating pulley 11 a radial free space 31 educated. With a centrifugal force ( 6th and 7th ) the respective centrifugal element 15th using up the radial free space 31 until it is in engagement with the one on the inner circumference of the ring of grooves 21 the non-rotating pulley 11 trained counter contour 29 come. In the radial space 31 is a ring spring 33 arranged according to the 8th is clamped with a predefined spring force F1 on the outer circumference of the support ring and in a rest position ( 5 ) the centrifugal elements 15th in their resting position.

Both on the outer circumference of the support ring and on the radially outer side of the centrifugal force elements 15th are spring grooves 35 formed in which the annular spring 33 is arranged.

If the centrifugal force is very high, the ring spring 33 Lift off radially outward from the outer circumference of the support ring. In order to maintain perfect ring spring positioning in this case, the 4th or 6th on the inner circumference of the ring of grooves 21 a circumferential spring groove 37 is formed. The ring spring lifts off the inner circumference of the support ring when there is a very strong centrifugal force 33 can therefore radially outward up to the inner circumference of the ring of grooves 21 Retract formed spring groove 37.

As from the spring force-speed diagram of the 8th shows is the ring spring 33 clamped with the predefined spring force F1 on the outer circumference of the support ring, the value of which is approx. 750 N by way of example. In the event of centrifugal force (i.e. in GB generator operation), the centrifugal force elements press 15th radially outwards until the locking position is reached ( 6th or 7th ). This leads to an expansion of the ring spring 33 , while building up the spring force up to a value of F2, which is in the 8th is approximately 1200 N by way of example. In the 8th sets the effect of the centrifugal force on the centrifugal force elements 15th at one speed of the switchable pulley 9 of approximately 270 min ^-1 . When a speed of approximately 330 min- ^{1 is reached} , the centrifugal force elements are 15th relocated to their locked position.

List of reference symbols

1

Electric machine shaft

3rd

Aggregates shaft

5

Internal combustion engine shaft

7th

Internal combustion engine-side pulley

9

switchable pulley of the electric machine shaft

11

non-rotating pulley of the electric machine shaft

12th

Basic body of the switchable pulley

13th

pulley on the unit side

15th

Centrifugal elements

16

Form-fitting contour of the respective centrifugal force element

17th

Support ring

19th

Installation space

21

Grooved wreath

23

Hub section

25th

Connecting flange

27

Guide channel

29

Counter contour

31

radial clearance

33

Ring spring

35,

37 spring grooves

39

Freewheel outside

40

Pivot bearing

41

Clamping elements

42

Pivot bearing

43

Freewheel inside

BKM

Internal combustion engine

RSG

Electric machine

mKK

mechanical air conditioning compressor

RBKM

Internal combustion engine belt drive

RmKK

Unit belt drive

A1

first drive direction of rotation

A2

second drive direction of rotation

L1, L2, L3, L4, L5

Load paths

K1

One-way clutch

K2

Centrifugal clutch

Claims (6)

Belt pulley arrangement with a switchable belt pulley (9) which is arranged on a drive shaft (1), in particular an electric machine shaft, and can be coupled to or decoupled from the drive shaft (1) in a torque-transmitting manner via a coupling device, depending on different operating modes (MB1, MB2, GB) of the pulley arrangement, wherein in a first operating mode, in particular a first motor operating mode (MB1), the coupling device couples the drive shaft (1) to the switchable pulley (9) in such a way that when the drive shaft rotates in a first drive direction of rotation (A1) forms a load path (L1) from the drive shaft (1) in the direction of the switchable pulley (9), wherein in a second operating mode, in particular a generator mode (GB), the coupling device connects the drive shaft (1) with the switchable pulley ( 9) couples in such a way that when the drive shaft rotates in the first drive The direction of rotation (A1) forms an opposing load path (L3) from the switchable belt pulley (9) into the drive shaft (1), with the coupling device separating the drive shaft (1) from the switchable pulley (1) in an additional operating mode, in particular a second motor operating mode (MB2). 9) is decoupled, so that when the drive shaft rotates in an opposite, second drive direction of rotation (A2), a load path (L5) along the drive shaft (1) is formed, with the load on the switchable pulley (9) being relieved, the clutch device having an overrunning clutch (K1 ) and a centrifugal clutch (K2) which, depending on the operating mode (MB1, MB2, GB), automatically provide a coupling or decoupling between the switchable pulley (9) and the drive shaft (1), the switchable pulley (9) is arranged with the radial interposition of the overrunning clutch (K1) on the drive shaft (1), and at least the centrifugal clutch (K2) est has a centrifugal force element (15) which can be acted upon by centrifugal force and which is adjustable between a rest position and a blocking position, and the centrifugal force element (15) in the blocking position engages a mating contour (29) of the drive shaft (1) and disengages it in the rest position is, characterized in that a non-rotatable belt pulley (11) is arranged on the drive shaft (1), that the two belt pulleys (9, 11) directly adjoin one another axially, and that the non-rotatable belt pulley (11) has a radially inner installation space (19) provides in which the centrifugal element (15) of the centrifugal clutch (K2) can be positioned. Pulley arrangement according to Claim 1 , characterized in that the drive shaft (1) is an electric machine shaft of an electric machine (RSG), that the non-rotatable belt pulley (11) is part of an aggregate belt drive (R _mKK ) which drives the non-rotatable belt pulley (11) with an auxiliary unit (mKK) connects, and that the switchable pulley (9) is part of an internal combustion engine belt drive (R _BKM ), which drives the switchable pulley (9) with an internal combustion engine (BKM). Pulley arrangement according to Claim 2 , characterized in that in the first motor operating mode (MB1) the electric machine (RSG) drives via its electric machine shaft (1) and the internal combustion engine belt drive (R _BKM ) in a first driving direction of rotation (A1) on the internal combustion engine (BKM), and that in the generator operating mode (GB) the internal combustion engine (BKM) drives via its internal combustion engine shaft (5) and the internal combustion engine belt drive (R _BKM ) in the first drive direction of rotation (A1) on the electric machine (RSG), and that in the second engine operating mode (MB2) drives the electric machine (RSG) via its electric machine shaft (1) and the unit belt drive (R2) onto the ancillary unit (mKK). Pulley arrangement according to Claim 3 or 2 , characterized in that the torque-transmitting locking function of the overrunning clutch (K1) is activated in the first operating mode (MB1), and its transmission-free freewheeling function is activated when the electric machine (RSG) is operated in a second driving direction of rotation (A2) opposite to the first driving direction of rotation (A1) , and / or that the torque-transmitting locking function of the centrifugal clutch (K2) is activated in the second operating mode (GB), and its transmission-free freewheeling function is activated when the electric machine (RSG) is operated in the opposite second drive direction of rotation (A2), and that in particular in the Additional operating mode (MB2), the electric machine (RSG) rotates in the second drive direction of rotation (A2), in which the freewheel function is activated in both the overrunning clutch (K1) and in the centrifugal clutch (K2), so that the Electric machine (RSG) the auxiliary unit (mKK) regardless of the internal combustion engine (BKM) drives. Belt pulley arrangement according to one of the preceding claims, characterized in that the installation space (19) is formed on the side of the non-rotatable belt pulley (11) facing the switchable belt pulley (9), and / or that the installation space (19) is between a radially outer grooved ring (21), a radially inner hub section (23) and a connecting flange (25) of the rotationally fixed pulley (11) is arranged, which connects the hub section (23) and the grooved ring (21) to one another, and that in particular the mating contour (29) on the Inner circumference of the ring of grooves (21) of the rotationally fixed pulley (11) is formed. Belt pulley arrangement according to one of the preceding claims, characterized in that the centrifugal clutch (K2) has a linear guide, by means of which the centrifugal element (15) can be adjusted between its rest position and its blocking position, and that, in particular to implement the linear guide, the switchable belt pulley (9) with a support ring (17) is axially extended, which in the assembled position protrudes into the installation space (19) of the axially adjacent rotationally fixed pulley (11), and / or that in the support ring (17) of the switchable pulley (9) at least one guide channel (27) is formed in which the centrifugal force element (15) is guided radially adjustable.

Images