JP2003530515A - Device for coupling at least one sub device and one main device - Google Patents

Abstract

The invention relates to a device for coupling at least one accessory (32), especially a starter generator, with a main drive (20), especially with an internal combustion engine. The at least one accessory (32) and the coupling device (26) are interlinked by means of a transmission (27). The device is provided with a planetary gear (38) that links the main drive (20) with the transmission (27), said planetary gear (38) being switchable between two gear ratios by means of a first clutch (53). The first clutch (53) is a free engine clutch and an internal geared wheel (50) of the planetary gear (38) can be locked in at least one direction of rotation by a second clutch (57).

Description

Detailed Description of the Invention

The invention relates to a device for connecting at least one sub-device and one main device, in particular a starter generator and an internal combustion engine.

A device for connecting a sub-device to a main device is already known from DE-A 1961291 A1. The known device has a planetary gear transmission (planetary gear transmission), and the sun wheel of the planetary gear transmission is connected to a drive shaft in a relatively non-rotatable manner. A planet wheel is arranged around the sun wheel, and the axle of the planet wheel is firmly connected to the belt wheel. A planet wheel is adapted to roll along the hollow wheel, which is connected to the clutch device. The clutch device is 2
It has two switching stages, in which the hollow wheel can be connected to the planet wheel in a non-rotatable manner in the first switching stage. In the second switching stage, the hollow wheel can be connected to the stationary frame via the clutch device. The clutch device can be switched using an electromagnet. The hollow wheel is rigidly connected to the planet wheel in a first position in which the electromagnet is not powered.
In the second switching position, the hollow wheel is rigidly connected to the frame.

A disadvantage of the above device is that the drive shaft of the internal combustion engine is always connected to the belt transmission. This is a disadvantage, in particular, when the sub-device is to be driven by a starter-generator that is motorisch betriebenable via a common belt drive when the internal combustion engine is stopped. . Another disadvantage of the known device is the need for an actuated switching element, here a magnetic clutch, for adjusting the transmission ratio of the planetary transmission. For this, the device must be actuated externally. As a further disadvantage, the active switching of the magnet clutch requires a continuous power supply, which results in additional energy consumption.

Advantages of the invention By using a device according to the invention having the features of the independent claims,
In the common belt transmission between the starter generator, the internal combustion engine and the further sub-device, the further sub-device can be driven even when the internal combustion engine is stopped, in which case the moment is Or, it is not transmitted to the main device. Thus, torque can be transmitted from a sub-device which can be operated in a dynamic manner, for example a starter generator, via the wheels of the device according to the invention to, for example, an air-conditioning compressor, in which case the moment is transmitted to the main device or the drive shaft of the main device. It will not be transmitted. This is particularly advantageous when the main device is shut off, i.e. the drive shaft of the main device is not rotating. This situation is the case when it is desired to continue conditioning the vehicle with the mechanically actuatable air conditioning compressor with the main device stopped.

Advantageous configurations of the device according to the main claim are possible due to the features of the dependent claims.

If the planet frame is non-rotatably connected to the drive shaft of the internal combustion engine, one transmission state between the drive shaft and the wheel or belt wheel is obtained, which in particular drives the drive shaft. This is an advantage when the shaft drives a starter generator, which acts as a generator, via a belt wheel.

On the other hand, a particularly high moment can be transmitted to the drive device when the electric motor of the starter generator is operated by switching the planetary gear device. If the hollow wheel is embodied as an intermediate ring, a second clutch can be arranged on the intermediate ring, so that the intermediate ring can take on another function. The intermediate ring is on the one hand part of the first clutch and at the same time part of the planetary transmission, and on the other hand the second component, for switching the device between the belt wheel and the drive shaft to the belt wheel. Can be switched according to the moment action of.

In particular, by applying a drive torque to the drive shaft via the wheel or belt wheel, a high transmission is obtained, and the moment action on the drive shaft is extremely high. On the other hand, when the drive shaft drives the starter generator via the belt wheel, the starter generator is driven in one transmission state. Therefore, it is advantageous if the first clutch and the second clutch have the same locking device.

The second clutch is preferably switchable independently of the first clutch, since the clutches can be disengaged independently of one another.

It is advantageous for the disengagement of the second clutch to release the rigid connection between the intermediate ring and the position-locking part, which can be removed from the belt wheel when the main unit is not driven. No torque is transmitted to the main device via the planetary gearing. In this case, a belt wheel is used as the turning roller.

Further advantageously, the rotating outer ring can be braked by the brake in the non-rotating state of the planet frame of the planetary transmission. When the outer ring is braked while the sun wheel is driven, the rotation pulse is transmitted to the drive shaft or the crankshaft, which allows so-called pulse starting of the internal combustion engine.

[0012]   Example description   Components having the same or the same function are given the same numeral.

FIG. 1 shows the arrangement of a main device 20 designed as an internal combustion engine. The main device (main unit) 20 has a drive shaft 23, which is connected to the device 26. The device 26 is connected via a transmission 27 to a sub-device 32 designed as a starter generator. The transmission 27 is embodied as a traction member transmission (Zugmittelgetriebe). Further, an air conditioning compressor 35 is driven as another sub device via the traction member 29.

FIG. 2 illustrates the principle of a first embodiment of the device 26. The device 26 has a planetary gear 38, which comprises a sun wheel 41, a planetary wheel 44, a planet frame 47 and a hollow wheel 50. The hollow wheel 50 is connected to the sun wheel 4 by the first clutch 53.
Can be connected to 1. The clutch 53 is formed as a freewheel. The clutch 53 allows the relative rotation of the sun wheel 41 with respect to the hollow wheel 50 in the first rotation direction and blocks the rotation in the second rotation direction, and the relative rotation is impossible in the second rotation direction. Relative rotation in the second rotational direction is prevented by sprags 54.
The hollow wheel 50 can be defined by a second clutch 56, which can be switched independently of the first clutch 53. To this end, in the illustrated embodiment, the pin 57 engages in the groove 58 of the hollow wheel 50. In the illustrated embodiment, the second clutch 56 is locked by the pin 57. This is necessary, for example, if one wishes to make a cold start. The cold start control locks the hollow wheel 50 by the second clutch 56 (external operation).

FIG. 3 is a vertical cross-sectional view of the device 26. Two sprags 54 to help understanding
And two planet wheels 44 are drawn in the plane of the drawing. The drive shaft 23 is coupled to the planetary frame 47 so as not to rotate relative thereto. As shown in FIG. 2, the planet frame 47 has three shaft pins 59, on which the planet wheels 44 are rotatably supported. The intermediate ring 62 is designed to function as a hollow wheel (ring gear) 50 on the one hand and an outer ring 65 of the first clutch on the other hand. The drive shaft 23 has a shaft journal 68 on which a hub 74 is rotatably supported. The hub 71 has a first axial section 74 which serves as the sun wheel 41 for the planet wheel 44. A second axial section 77 of the hub 71 serves as an inner ring 80 of the first clutch 53. The first clutch 53 is formed by an outer ring 65, a sprag 54 and an inner ring 80. A disk-shaped area (Bereich) 86 is connected to the hub 71, and a substantially cylindrical section 89 is connected to the area. The substantially cylindrical section 89 is
Together with the disc-shaped area 86 and the hub 71, a wheel 92 is formed, which serves as a sheave for the belt 29. This makes the wheel 9
2 is associated with one transmission part of the planetary transmission 38. Intermediate ring 6
2. The hollow wheel 50 can be fixed (lockable) by the clutch 56 using the pin 57 and the groove 58. A clutch 56 is mounted on the outer part, the crank casing of the internal combustion engine.

When the intermediate ring 62 is unlocked, as shown in FIGS. 2 and 3, the wheel 92 or the sun wheel 41, as shown in FIG.
That is, the drive shaft 23 is rotated in the first rotation direction, and the drive shaft 23 is locked based on the outer rotation resistance, so that the first clutch 53, on the one hand, causes relative rotation between the sun wheel 41 and the hollow wheel 50. On the other hand, the hollow wheel 50 rotates. The planet frame 47 does not rotate. The planet wheel 44 transmits the rotational movement of the sun wheel 41 to the hollow wheel. Clutch 5
With 6 open, under ideal conditions, ie without acceleration and without friction, no torque acts on the drive shaft 23. Only in the case of friction and acceleration of the rotating mass, a slight torque occurs. This will be described with reference to FIG. 1. The sub device 32 acting as a motor utilizes the device 26 or the wheel 92 as a turning roller to drive only the air conditioning compressor 35 and rotate the main device 20 or the internal combustion engine. There is no need to be. Such a position of the second clutch 56 is particularly suitable when the main device 20 is not in the operating state but it is desired to drive the air conditioning compressor 35. Such an example is applicable to an energy-saving vehicle including the main device 20 or the device shown in FIG. 1 when the internal combustion engine is not in operation but air conditioning of the vehicle interior is desired.

The device 26 shown in FIG. 4 is fixed by the second clutch 56 or the intermediate ring 62 of the clutch and the hollow wheel 50. In this case, when the wheel 92 is driven by the sub device 32 by a motor, that is, as a starter, the sun wheel 41 drives the planet wheel 44 and rolls along the hollow wheel 50 to which the planet wheel is fixed.
At the same time, the planet frame 47 is moved in the first rotational direction. The planet frame 47 is the drive shaft 23.
Torque acts on the drive shaft 23 due to its non-rotatable connection. Therefore, when the main device 20 is an internal combustion engine and the drive shaft 23 is, for example, a crankshaft, the internal combustion engine can be started. In this case, the first clutch 53 is opened. The planetary gear 38 provides a transmission when the hollow wheel 50 is held stationary, which increases the torque, which is very advantageous for starting the internal combustion engine.

Even in the above-mentioned position on the other side, the internal combustion engine can drive the planet wheel 44 via the planet frame 47, thereby driving the sun wheel 41 or the wheel 92. Therefore, the first outer ring 65 locked by means of the clutch 56 also allows the sub-device 32 to operate in a power generation mode. Here too, the freewheel 53 rotates and, due to the high transmission ratio, the wheel 92 rotates at a higher speed than the drive shaft 23. Therefore, even when the sub device 32 has a low engine speed, it produces a large electric output. This takes place only in the case of the actively switchable clutch 56, not in the case of the freewheel clutch 56 (FIG. 7).

FIG. 5 shows a second embodiment. In the second embodiment, the second clutch 56 is the brake 95. As shown in FIG. 5, when the hollow wheel 50 or the intermediate ring 62 is in the non-braking state, the wheel 92 is electrically driven by the sub device 32, so that the air conditioning compressor 35 (see FIG. 1, see FIG. 1) even when the engine is off. ) Can be driven. In this case, the function is the same as described in FIG. When the engine is turned off, the sub-device 32 is electrically operated, and the brake is opened, the device 2 is operated.
Even if 6 is driven (air conditioning when stopped), no torque that would cause a start will act on the drive shaft 23. Due to these external conditions, the brake remains unoperated. When the brake 95 is operated based on an external condition (starting request), that is, when an increasing braking force is generated in the intermediate ring 62, the motion state changes. The sun wheel 41, which continues to rotate in the first rotation direction, not only causes the rotational movement of the planet wheel 44, but also applies a braking force to the intermediate ring 62 and thus brakes the hollow wheel 50, and thus the planet wheel frame 47. 6 also causes rotation in the first direction of rotation of FIG. The stronger the braking action on the intermediate ring 62, the faster the rotation of the planet frame 47 in the first direction of rotation. The internal combustion engine can be started when the torque generated via the planetary frame 47 and the rotational speed of the planetary frame 47 reach the minimum starting rotational speed of the internal combustion engine. The quicker the brake 95 stops the hollow wheel 50 or the intermediate ring 62, the better the kinetic energy of the subsystem 32 will be for starting or pulse starting the internal combustion engine.

FIG. 7 shows a cross section of the third embodiment. The third embodiment has a sun wheel 41, a planet wheel 44, a planet frame 47 and a hollow wheel 50 or an intermediate ring 62, as in the previous embodiment. The first clutch 5 is provided between the sun wheel 41 and the intermediate ring 62.
3 is working. The first clutch 53 prevents rotation of the intermediate ring 62 with respect to the sun wheel 41 in the first rotation direction. Unlike the previous embodiments, the intermediate ring 62 is the inner ring 98 of the second clutch 56. Similarly, the second clutch 56 can be switched without being influenced by the first clutch 53.
A second outer ring 101 is non-rotatably connected to the outer part, here also the crank casing. The second clutch 56 is arranged between the second outer ring 101 and the intermediate ring 62, and the intermediate ring 62 is rotatable with respect to the second outer ring 101 in the first rotation direction. Depending on the first clutch 53, the sprag 54 is adapted to prevent the inner ring 98 from rotating in the second rotational direction relative to the second outer ring 101. In the otherwise unchanged arrangement, see also FIG. 1, the power generation operation takes place as follows: A drive shaft 23 connected to a planet frame 47 drives the planet frame in a first rotational direction. ,
Figure 8. The first clutch 53 is locked based on the moment or force state in the first clutch 53. This means that the sun wheel 41 rotates as a block together with the planet frame 47 and the intermediate ring 62 or the first outer ring 65, i.e. the sun wheel 41 rotates at the same speed as the planet frame 47. On the other hand, the second clutch 56 enables the second inner ring 98 or the intermediate ring 62 to rotate in the first rotation direction based on the motion state (internal condition). Rotating sun car 4
The wheel 92 is entrained by 1, and the sub device 32 is operated to generate electric power. The air-conditioning compressor 35 is also operated by the traction member transmission device. In this case, the rotation ratio between the drive shaft 23 or the crankshaft and the wheel 92 is 1.

When the starting operation is performed in the third embodiment (see also FIG. 9), the solar car 41 is moved to the sub device 3
It is electrically driven by 2 in the first direction of rotation. Due to the rotation resistance of the planet frame 47 connected to the stationary drive shaft 23, the planet frame 47 overcomes the rotation start moment of the main device 20 or the internal combustion engine at a reduced rotation speed with respect to the sun wheel 41. Rotate. Based on the force or moment state, the first clutch 53 causes the sun wheel 41 to move.
To rotate in a first direction of rotation. On the other hand, the second clutch 56 is locked in the second rotation direction, that is, in the direction opposite to the first rotation direction based on the motion state (internal condition), and as a result, the intermediate ring 62 does not move. , See also FIG.

The difference between the fourth embodiment and the third embodiment is that the second outer ring 101 is not fixed to the surroundings, that is, to the crank casing of the internal combustion engine. See also 10. A second outer ring 101 as an outer part is able to connect a third clutch 104, which is formed as a lock lever, to a stationary position. In the fourth embodiment, when the sub device 32 is in the stopped state of the main device 20 or the internal combustion engine, for example, when the wheel 92 is driven as in FIG. 1, the air conditioning compressor 35 operates with the third clutch opened. To be done. In this case, the sun wheel 41 is driven by the sub device 32 and rotates in the first rotation direction. Planet frame 4
7 is held stationary by the drive shaft 23, which is also immovable, and also remains immobile. The rotating planetary wheel 44 causes the intermediate ring 62 to rotate in the second rotational direction, and the second outer ring 10 to rotate through the locking second clutch 56.
Carry 1 As a result, the air conditioning compressor 35 can be driven even when the main device 20 is not driven or the drive shaft 23 is not rotating.

When the third clutch 104 holds the second outer ring 101 immobile by the engagement of the locking lever in the groove 58, the same previously mentioned motion state as in the third embodiment is obtained.

The fifth embodiment shown in FIG. 11 has a third clutch 104 in the form of a brake instead of the third clutch 104 in the form of a lock lever. If the clutch 104 is open, that is, if no braking moment is exerted on the second outer ring 101, the same motion state will occur in the fourth embodiment as if the lock lever were not engaged in the groove 58. ing. In the fifth embodiment, when the sub device 32 drives the wheel 92 with the clutch 104 first opened, the drive shaft 23 is not entrained via the planetary frame 47. In contrast, the clutch 104 has the second outer ring 1
01 is brought into contact with the planetary frame 47, and thus the drive shaft 23 is moved to the second position.
If the clutch is locked, it will be gradually accelerated. This additionally causes the rotation pulse of the sub-device 32 to be transmitted via the wheel 92 to the planet frame 47 and thus to the drive shaft 2.
3 which in turn accelerates the drive shaft very strongly for starting the main unit 20 or the internal combustion engine.

To improve the device 26, it is also possible to provide a damping member 107 between the drive shaft 23 and the planet frame 47 for vibration damping, see also FIG. The damping member 107 may be used so that the coupling between the drive shaft 23 and the planetary frame 47 is relatively non-rotatable.

The sixth embodiment of FIG. 12 shows a longitudinal section. The drive shaft 23 of the main device 20 has a drive shaft end 110 formed in a cylindrical ring shape, and a bearing 116 is arranged on a cylindrical outer periphery 113 of the drive shaft end. A bearing 116 supports the hollow wheel 50 on the outer circumference of the bearing, which here forms the outer ring 65. A shaft pin 59 for the planet wheel 44 is attached to the end surface of the drive shaft 23. The teeth of the planet wheel 44 mesh with the teeth of the hollow wheel 50. A first clutch 53 in the form of a freewheel clutch is arranged in the hollow cylinder notch 121. Both the planet wheel 44 and the first clutch 53 cooperate with the axial journal 124 of the wheel 92. To this end, the axial journal 124 has an axial first section 74,
The section is formed as a sun wheel 41 and cooperates with a planet wheel 44. A second axial section 77 cooperates with the first clutch as an inner ring 80. The hollow wheel 50 has a cylindrical section 127, which serves as a friction cylinder 130 for the second clutch 56, which is designed as a friction clutch 133. The friction clutch 133 is formed here as a friction belt brake, the friction belt 139 of which is shown in the plane of the drawing for the sake of clarity. Details of the second clutch are shown in FIG.

As is apparent from FIG. 13, the second clutch 56 has a friction cylinder 130 and a friction belt 139. In principle, the friction clutch 133 is the friction belt 1
The friction belt is connected to the first member 146 of the four-bar linkage 149 via two hinges 142 and 143. The four-bar linkage 149 further has a second two member 152, which is the third member 1 whose position is fixed.
It is attached to 55 so as to be rotatable. Further, the second clutch 56 is the adjustment member 1
58, the adjusting member is adapted to change the position of the first member 146 via a member (not shown).

When the main device 20 is started by the sub device 32 (external condition), the sub device 32 drives the sun wheel 41 in the first rotation direction via the transmission device 27 (counterclockwise rotation). The drive shaft 23, and thus the planet frame 47, is unlikely to rotate. Friction clutch 13
3, and thus the first member 146 is adjusted so as not to allow the rotation of the hollow wheel 50 in the second rotation direction (right rotation). As a result, the sun wheel 41 drives the planet wheel 44 supported by the hollow wheel 50 based on the motion state in the planet wheel transmission, and as a result, the planet frame 47 rotates in the first rotation direction. The planet frame 47 rotating in this way rotates the crankshaft or the drive shaft 23, whereby the internal combustion engine or the main device 2 is rotated.
0 is started. In this case, the freewheel clutch or the first clutch 5
3 enables relative rotation between the sun wheel 41 and the planet frame 47. The rotation angle of the planet frame 47 is reduced to approximately one third as compared with the angular velocity of the wheel 92. by this,
The torque acting on the drive shaft 23 is almost tripled.

When the main device 20 or the internal combustion engine shifts to self-driving, a force direction change occurs between the planet wheel 44 and the hollow wheel 50 via the drive shaft 23 and the planet frame 47 connected to the drive shaft, As a result, the friction belt 139 moves away from the friction cylinder 130,
Braking no longer occurs. At the same time, the planetary frame 47 or the drive shaft end 110 carries the sun wheel 41 through the cylindrical inner surface of the drive shaft end and the first clutch 53, and also through the axial second section 77. This in turn drives the sub-device 32 and thus the starter generator via the wheel 92 or the cylindrical section 89 of the wheel, so that the starter generator can be driven. In this case, the second clutch 56 is open.

In the case of low engine speeds of the internal combustion engine or the main device 20, it is advantageous to increase the current emission of the sub-device 32, which is designed as a starter generator.
For this purpose, in the exemplary embodiment, a simple switching of the first member 146 using the adjusting member 158
That is, the second clutch 56 can be closed again by moving the first member 146 to the left. In this case, the hollow wheel 50 is locked during driving by the drive shaft 23 or the planet frame 47, and as a result, the planet frame 47 drives the sun wheel 41 at an increased angular velocity (approximately three times). In this case, the starter generator or the sub device 32 is driven at a high rotation speed via the wheel 92 and the transmission device 27, and as a result, a large amount of current can be generated in the power generation operation.

When the speed of the internal combustion engine is increased, the subsystem 32 or the starter generator must not be overloaded during operation with a high transmission stage. High transmission stages theoretically impose a high rotational speed on the rotor of the starter generator, which results in the rotor being damaged by centrifugal loads. This must be avoided. In this connection, the higher transmission stage has to be appropriately switched to the lower transmission stage. Because of this, the adjustment member 158 is not movable. This is possible only by torque conversion in the sun wheel 41. That is, before the high transmission stage is switched to the low transmission stage, the starter generator is operated as a motor for a short time to generate a torque change in the hollow wheel 50 via the planetary wheel 44, thereby loosening the friction belt 139, and at the same time. First, the adjustment member 158 is used to move the first member 146 to the neutral position. The first member 146 is then tilted to the position shown in FIG. 13 during a brief motor run of the subsystem 32 to achieve low transmission. Therefore, the tightening of the friction belt 139 locks the hollow wheel 50 under the simultaneous driving action of the sub-device 32. With the introduction of such a switching process, a positive closing of the second clutch 56 is possible, so that the sub-device 32 can be switched back into a power-generating operation. After the second clutch 56 is closed, the sub-device 32 is driven with low transmission.

If the vehicle is equipped with, for example, a so-called automatic start / stop device,
With such a device it is possible to achieve so-called standstill air conditioning as already described in the previous embodiments. When the internal combustion engine is stopped, the sub-device 32, for example, also drives the belt-driving air conditioning compressor with the friction clutch 133 or the second clutch 56 open, whereby the stop-time air adjustment is achieved. . In this case, the hollow wheel 50 rotates unhindered. So-called pulse starting of the internal combustion engine is possible using the device shown in FIGS. For this purpose, the sub device 32 is used as a drive unit. In this case, the friction clutch is first opened and the friction belt 139 is not in contact. The solar car 41 is the sub device 3
The hollow wheel 50 is rotated via the planetary frame 47 that is driven via 2 and is not moved (second rotation direction). The subsystem 32 accelerates to an appropriately high rotational speed, so that the entire drive system from the subsystem 32 to the hollow wheel 50 has sufficient kinetic energy so that after actuation of the friction clutch 133 the planet frame 47 is acted upon. The torque to start the internal combustion engine. In this case, the first member 146 occupies the position shown in FIG. 13, that is, the position slightly moved to the right.

Another embodiment is shown in FIG. This embodiment is a modification of the embodiment of FIG. While the second clutch 56 of FIG. 7 is independent of rotational acceleration of the intermediate ring 62, the second clutch 56 of the embodiment of FIG. 14 locks in relation to the rotational angular velocity of the intermediate ring 62. For this purpose, the sprags 54 are supported in the recess 161 with their radially inwardly directed ends and are pivotable. Alternatively, the sprag 54 may be pivotally mounted using a hinged bearing between the sprag and the intermediate ring 62. The compression spring 162 supported by the intermediate ring 62 holds the sprag 54 in the starting position, and the sprag 54 is not in contact with the second outer ring 101. When a drive moment is introduced via the sun wheel 41 into the planetary wheel transmission 38 via the electrically operated sub-device 32 to start the internal combustion engine or the main device 20, the hollow wheel is moved with high acceleration. It The sprag 54 moves based on its own inertial mass and is eventually moved to the blocking position (see FIG. 15). This locks the hollow wheel 50 or the intermediate ring 62. The planetary transmission 38 now transmits the torque of the sub-device 32 to the drive shaft 23, so that the main device 20 is started with the transmission ratio of the planetary transmission and thus with a high torque. The second clutch 56 (inertia-switching freewheel) is based on its characteristics and allows the driveshaft 23 to overtake, as normally occurs during the starting process of an internal combustion engine. After such overtaking of the drive shaft 23, the drive shaft 23 is retarded again with a high acceleration, so that
The second clutch 56 is again moved to the blocking position.

During the power generation operation of the sub device 32, the moment state in the planetary gear transmission 38 changes. The second clutch 56 is not locked, and the hollow wheel 50 can freely rotate. In this state, the planetary gear device 38 does not transmit any torque. Therefore, the rotation of the sun wheel 41 decreases and reaches the rotation speed of the drive shaft 23. When that happens,
The first clutch 53 operates. Another sub-device, eg air conditioning compressor 35
Are driven via the transmission 27. When the air conditioning compressor 35 is driven by the sub device 32 without transmitting the drive moment to the drive shaft 23,
First, only a small torque is produced by the sub-device 32. The planetary gear 38 is moved slowly and thus the hollow wheel 50 or the intermediate ring 62.
Suffers only a slight acceleration. The spring 162 holds the sprag 54 in a rest position and the second clutch 54 is not locked.

FIG. 16 partly shows another embodiment starting from the embodiment of FIG. The second clutch 56 is replaced by the second clutch 56 shown in FIG. 16 with respect to the embodiment of FIG. The intermediate ring 62 or the inner ring 98 is replaced by a second inner ring 98 with at least one recess 161 on the cylindrical outer circumference, into which the sprag 54 can be inserted. A retainer 164 formed in a ring shape is arranged between the inner ring 98 and the outer ring 101. Cage 1
64 has an end surface 167 from which a small pin 170 extends axially. The pin 170 synchronizes the movement of the sprag 54. In this case, the pin 170 is located in the recessed notch 173 in the sprag 54 in the assembled state, see also FIG. 16A. The sprag 54 has, on the one hand, the actual tightening portion 176, the tightening portion being arranged on one side of the pin 170, and further having a lever portion 179, the lever portion being a recessed notch. 173 is provided. The lever portion 179 is arranged on the other side of the pin 170, so that the clamping portion 176 and the lever portion 179 are substantially diametrically opposed to each other. The center of gravity of the sprag 54 is located on the left side of the recess 161. Lever part 179
A compression spring 185 is supported on the. When the inner ring 98 is rotated in the first rotation direction (clockwise direction), the sprag 54 is rotated clockwise into the recess 161, but the sprag 54 does not lock the second clutch 56. No, and thus the inner ring 98 is free to rotate.

The second clutch 56 is not locked even when the inner ring 98 makes a complete rotational movement in the second rotational direction at a constant rotational speed. When the inner ring 98 is moved with a large angular acceleration in the second rotation direction (counterclockwise direction), the tightening portion 17
6 is swiveled into the recess 161, so that the clutch 56 locks. This is true for low rotational speeds. When the rotational speed is extremely high, the centrifugal force of the sprag 54 causes the second clutch 56 to be activated despite the rotational acceleration in the second rotational direction.
Block the lock. The mass of the lever portion 179 prevents the locking action of the sprag 54 during rotation of the inner ring 98. Sub device 32, transmission device 27, device 26
Also, in the main device, it is possible to prevent the hollow wheel 50 in which the drive portion of the electrical sub device 32 rotates from being stopped when the moment impact occurs and the main device 20 being started. The retainer 164 serves to synchronize the movement of the sprags 54 and thereby evenly distribute the load to all sprags 54.

FIG. 17 shows another modification of the second clutch 56. Inner ring 98
Similarly, a sprag 54 is arranged between the outer ring 101 and the outer ring 101. In the starting and resting positions shown in FIG. 17, a bistable spring 188 causes the retainer 164 to engage the pin 170.
With some rotation, thus crimping the pin 170 onto the sprag 54 and not contacting the sprag 54 with the outer ring 101, which results in a tightening effect. Now, when a strong angular acceleration of the inner ring 98 occurs in the second rotational direction, one position of the bistable spring 188 is overcome, so that the retainer 164 moves relative to the inner ring 98 relative to the inner ring 98. In the direction of rotation of 1, so that pin 170 releases sprag 54, which causes second clutch 56 to lock again. A lever 191 is pivotally attached at one end to the inner ring 98 with a central bolt portion 194 of the lever 1 directed radially outward of the cage.
It is possible to work within 97. Now, when a strong angular acceleration of the inner ring 98 occurs in the second rotational direction, the spring 188 extends for a predetermined length and the sprag 5
4 also moves in a second rotational direction relative to the pin 170 to contact the outer ring 101, see also FIG. At the same time, the bistable spring 188 changes position to assume a second position, which defines the relative position of the retainer 164 and the inner ring 98. In this case, the lever 191 is moved or, at the same time, pivoted in the first direction of rotation about the pivot point of the inner ring 98, so that the bolt portion 194 simultaneously acts radially inward in the groove 197. When the inner ring 98 is again moved in the freewheel direction, ie the first rotational direction, the centrifugal force of the mass 199 of the lever 191 acts and the retainer 164 or the pin 170 is pressed against the sprag 54 again, whereby The sprag is returned to the starting position.

A final example is shown in FIG. The device 26 also has a planet frame 47 connected to the drive shaft 23, and a planet wheel 44 is arranged on a shaft pin 59 of the planet frame. Here again, the planet wheel 44 meshes with the hollow wheel 50, and the hollow wheel is the hollow wheel support 2
00 is arranged so as to be movable in the axial direction. In this case, the hollow wheel 50 is different 2
19 may occupy one position, one in the position shown in FIG. 19 and the other in the position moved to the right in FIG. 19A, in this case the second clutch 5 in the position moved to the right.
6 works. In this case, the second clutch 56 is fixed to the hollow wheel 50 and the fixed portion 2
It works with 03. The second clutch 56 is formed by the first shape connecting member 206 and the second shape connecting member 209 of the position-fixed part 203. The planetary transmission 38 here has beveled teeth, so that an axial force is generated from the torque transmitted. The position of the hollow wheel 50 is switched by the torque transmitted from the planetary wheel transmission device 38. A spring loaded locking member 212 allows adjustment of a predetermined torque threshold for switching. In this case, the threshold is defined by the spring force and the geometry of the groove 213 that receives the locking member 212. The switching threshold values for the engagement and disengagement of the second clutch 56 may be defined independently of each other.

The second clutch 56 is locked by transmitting the acceleration of the wheel 92 to the acceleration of the hollow wheel 50 and the hollow wheel carrier 200 by means of the planetary wheel transmission 38. The transmission torque is defined based on the inertial and angular acceleration law of rotational acceleration of the hollow wheel 50 and the hollow wheel carrier 200. When the torque exceeds a predetermined threshold value, the hollow wheel 50
Are moved to the locked position. Such a process is canceled when the internal combustion engine or the main device 20 is started.

The second clutch 56 is opened by producing a negative torque via the wheel 92 and being received by the locked hollow wheel 50. When the torque exceeds a predetermined threshold value, the hollow wheel 50 is moved to the open position. This process is canceled, for example, when the sub device 32 is switched to the power generation operation.

By appropriately controlling the sub device 32, it is possible to arbitrarily control the position of the hollow wheel 50. As a result, the transmission state of the planetary gear device 38 is arbitrarily switched. When the motor speed is low, the sub device 32 is adjusted to a high transmission stage,
This allows a high output of the sub-device 32.

FIG. 20A shows the locking member in the axial direction. The locking member is a hollow car support 20
0 around the outer periphery of the hollow wheel 50 and the position-fixed portion 203
It is arranged between 209. The locking member 215 includes a leaf spring portion 218.
At rotational speeds above a predetermined threshold, the leaf spring portion 218 is deflected outward by centrifugal force to lock the axial position of the hollow wheel 50 of FIG. 20B. The rotational speed threshold itself may be adjusted by preloading the leaf spring 218. The starter generator 32, the device 26, and the air conditioning compressor 35 are the pulling members (pulling members) 2
They are connected to each other via 9. Both belts and chains are suitable as traction members 29. Starter generator 32, device 26 and air conditioning compressor 35
A gear transmission can also be used instead of a traction member transmission in which the two are connected to each other by a traction member 29.

In the embodiment shown in FIG. 21, the starter generator 32 is connected via a gear 110 to a wheel 92, which is also formed as a gear. The air-conditioning compressor 35 is coupled to the gear 113 so as not to rotate relative to it, and is coupled to the wheel 92. The gear 110 may be indirectly connected to the wheel 92 via the gear 113 depending on the desired transmission ratio. As another example, the gear 110 is replaced by the gear 113.
It is also possible to arrange it between the wheel and the wheel 92.

[Brief description of drawings]

FIG. 1 shows a first arrangement of a main device and two sub-devices with a device according to the invention.

[Fig. 2]   FIG. 1 shows a first embodiment of the device according to the invention.

[Figure 3]   FIG. 1 shows a first embodiment of the device according to the invention.

[Figure 4]   FIG. 1 shows a first embodiment of the device according to the invention.

[Figure 5]   FIG. 3 shows a second embodiment of the device according to the invention.

[Figure 6]   FIG. 3 shows a second embodiment of the device according to the invention.

[Figure 7]   The figure which shows a 3rd Example.

[Figure 8]   The figure which shows a 3rd Example.

[Figure 9]   The figure which shows a 3rd Example.

[Figure 10]   The figure which shows a 4th Example.

FIG. 11   The figure which shows a 5th Example.

[Fig. 12]   The figure which shows a 6th Example.

[Fig. 13]   Sectional drawing of the 6th Example along line XIII-XIII of FIG.

FIG. 14   The figure which shows a 7th Example.

FIG. 15   The figure which shows a 7th Example.

FIG. 16   The figure which shows an 8th Example.

FIG. 16A   The figure which shows an 8th Example.

FIG. 17   The figure which shows the 9th Example.

FIG. 18   The figure which shows the 9th Example.

FIG. 19   The figure which shows the last Example.

FIG. 19A   The figure which shows the last Example.

FIG. 20A   FIG. 20 is a detailed view of the embodiment of FIG. 19.

FIG. 20B   FIG. 20 is a detailed view of the embodiment of FIG. 19.

FIG. 21 shows a second arrangement of a main device and two sub-devices with a device according to the invention.

[Explanation of symbols]

20 main device, 23 drive shaft, 26 device, 32 sub device, 35 air conditioning compressor, 38 planetary gear transmission (planetary wheel transmission or planetary gear transmission), 41 sun wheel (sun wheel or sun gear), 44 planet Car (Planetary Wheel or Planetary Gear), 47
Planetary frame, 50 Hollow wheel (ring wheel, ring gear), 53 Clutch, 54
Sprag, 56 clutch, 57 pin, 58 groove, 59 shaft pin, 62 intermediate ring, 74 section, 77 section, 80 inner ring, 92 wheel, 95
Brake, 98 middle ring, 101 second outer ring, 104 clutch, 107 damping member, 110 drive shaft end, 113 outer circumference, 116 bearing, 12
1 notch, 124 shaft journal, 127 section, 130 friction cylinder,
133 friction clutch, 139 friction belt, 142, 143 hinge, 146
Member, 149 Four bar link, 158 Adjustment member, 161 Recess, 162 Compression spring, 164 Retainer, 170 pin, 173 Notch, 176 Tightening portion, 179 lever portion, 185 Compression spring, 188 spring, 191 lever, 1
94 bolt portion, 197 groove, 199 mass, 200 hollow car support, 203
Part, 206, 209 shape connecting member (meshing member), 212 locking member,
213 groove, 215 locking member

─────────────────────────────────────────────────── ─── Continued front page    (81) Designated countries EP (AT, BE, CH, CY, DE, DK, ES, FI, FR, GB, GR, IE, I T, LU, MC, NL, PT, SE, TR), OA (BF , BJ, CF, CG, CI, CM, GA, GN, GW, ML, MR, NE, SN, TD, TG), AP (GH, G M, KE, LS, MW, MZ, SD, SL, SZ, TZ , UG, ZW), EA (AM, AZ, BY, KG, KZ, MD, RU, TJ, TM), AE, AL, AM, AT, AU, AZ, BA, BB, BG, BR, BY, CA, C H, CN, CU, CZ, DE, DK, EE, ES, FI , GB, GD, GE, GH, GM, HR, HU, ID, IL, IN, IS, JP, KE, KG, KP, KR, K Z, LC, LK, LR, LS, LT, LU, LV, MD , MG, MK, MN, MW, MX, NO, NZ, PL, PT, RO, RU, SD, SE, SG, SI, SK, S L, TJ, TM, TR, TT, UA, UG, US, UZ , VN, YU, ZA, ZW

Claims (12)

[Claims] 1. At least one sub-device (32), in particular a starter generator and one main device (20), in particular a device for connection to an internal combustion engine, wherein the at least one sub-device (32). And a coupling device (26) are connected to each other by a transmission device (27) and are provided with a planetary gear device (38), the planetary gear device comprising a main device (20) and a transmission device (20). 27), in which the planetary transmission (38) is switchable between two transmission states by means of the first clutch (53), the first clutch (53) ) Is a freewheel clutch, characterized in that the hollow wheel (50) of the planetary transmission (38) is lockable by a second clutch (56) in at least one direction of rotation. A device for connecting one sub device and one main device. 2. The planet frame (47) is connected to the drive shaft (23) of the main device (20), in particular to the crankshaft of the internal combustion engine, in such a way that it cannot rotate relative to it, and is transmitted via the sun wheel (41). 2. The device as claimed in claim 1, wherein torque can be transmitted between the device (27) and the planetary transmission (38). 3. The first clutch (53) is a sun wheel () for a hollow wheel (50).
Device according to claim 1 or 2, wherein the relative rotation of 41) is enabled in the first direction of rotation or blocked in the second direction of rotation. 4. A second clutch (56) between the hollow wheel (50) and the outer part.
4. The device as claimed in claim 1, wherein the clutch is arranged as a freewheel to allow the hollow wheel (50) to rotate in at least a first rotational direction. 5. A second clutch (56) is operated to enable rotation of the hollow wheel (50) in a second direction of rotation. The described device. 6. The second clutch (56) is adjustable as a freewheel in relation to external actuation as a freewheel in one direction of rotation or in the other direction of rotation or as a freewheel. The apparatus according to claim 1. 7. The second clutch (56), which is embodied as a freewheel, is adapted to release or lock the hollow wheel (50) in connection with internal operation. The apparatus according to item 1. 8. A device according to claim 7, wherein the internal operation is the rotational speed or acceleration of the hollow wheel (50). 9. Device according to claim 4, wherein the hollow wheel (50) cannot be connected above the threshold of internal operation. 10. The outer part is a second outer ring (101), which outer ring is connectable to the fixed part by a third clutch (104). The described device. 11. At least one rotatable outer ring (65, 101).
Device according to any one of the preceding claims, wherein the device can be braked by a brake. 12. Device according to claim 1, wherein the sub-device (32) is drivable without the opposing moment of the main device (20).