DE2557243A1 - POWER TRANSMISSION DEVICE WITH CHANGEABLE TRANSMISSION - Google Patents

Description

PATENTANWÄLTE ZENZ & HELBER D 4300 ESSEN 1 AM RUHRSTEIN 1 TEL .: (02 01) 4126 87 Page _ 4. - G 828

GKN TRANSMISSIONS LIMITED Chester Road, Erdington, Birmingham B24 ORB. England

Power transmission device with variable translation

The invention relates to a power transmission device with a variable translation, in which one of a drive machine driven hydrokinetic torque converter and an output shaft are provided and one in the translation Infinitely variable mechanical gear and a direction of rotation change gear are arranged in series between the torque converter and the output shaft.

The expression "in the translation steplessly variable mechanical transmission" is understood to mean a transmission, the one to convert a constant input speed into a continuously variable output speed within a certain range able. Examples of such transmissions are so-called belt or pulley transmissions, in which a belt or a chain over a rotatable disk with changeable effective radii or on two disks with changeable effective radii Radii runs, and also friction gears, in which the rotational movement is frictional from one metallic part to the other, often via an intermediate link. The term "selectively operable reversing gearbox" refers to a gearbox understood about the the output shaft either in the same direction as the gearbox input shaft or in the

Z / bu.

© 09827/0694

Opposite direction can be driven selectively.

In a power transmission device of the type specified above, it is known in the transmission train one behind the other a prime mover, the torque converter, the reversing gearbox and a pulley drive with two variable pulleys driving the output shaft to arrange.

This known arrangement has two guard parts. The first disadvantage is that the power transmission device builds longer than necessary in the axial direction of the pulleys. This is because the torque converter, the reversing gearbox and a belt pulley of the belt drive are one behind the other are arranged on the same axis.

The second disadvantage of this arrangement is that if the power transmission device suddenly stops, e.g. in the event of an emergency braking in the case of the installation of the power transmission device in a motor vehicle, the power transmission device can be stopped at a high gear ratio of the continuously variable transmission. The turning direction— Change-speed transmission normally has means for disconnecting the drive from the torque converter. However, the The ratio of a continuously variable mechanical gear can only be changed when the drive is rotating, with the result that the power transmission device in the event of a stop started with a high gear ratio of the continuously variable mechanical transmission at the same high gear ratio must become. This is particularly unfavorable when the power transmission device is used in a motor vehicle.

It is therefore the object of the present invention to provide a power transmission device of the type specified at the outset, which on the one hand have a comparatively compact design

609 8 2 7/0694

allows and on the other hand eliminates the last-mentioned disadvantage of known power transmission devices is.

According to the invention it is provided for this purpose that the continuously variable mechanical transmission from the torque converter is driven directly and in turn drives the output shaft via the change-over gearbox and that the direction of rotation change gearbox has a neutral position in which the output shaft of the continuously variable mechanical transmission is separated.

It has been found that by arranging the direction of rotation change gear between the continuously variable mechanical transmission and the output shaft, instead of between the torque converter and the continuously variable mechanical transmission, a more compact design is possible.

The power transmission device preferably has a clutch device assigned to the torque converter on that to interrupt the drive connection Torque converter can be operated selectively. The clutch can be between the impeller and the output shaft of the converter be arranged. The clutch and the direction of rotation change gear can preferably be operated simultaneously in such a way that that the drive connection is interrupted via the torque converter when the output direction is changed. The torque converter can also have a lock-up clutch.

The continuously variable mechanical transmission is preferably designed as a “belt pulley drive ¹¹ , in which a chain runs on two rotatable disks, the effective radii of which can be changed two parallel axes of the mechanical

609827/0694

drove only the torque converter and a pulley are arranged with the associated adjustment means, while the other axis of the transmission is the other pulley with associated. Adjusting means and the direction of rotation change gear carries.

If the transfer train is arranged in a U-shape, there are two components on each U-leg, namely the torque converter and the input disk of the mechanical transmission on one leg of the U-shaped transmission pin and the direction of rotation change gear and the output pulley on the other leg of the U. From it it follows that the total length of the U is less than in the known case where three components are arranged on one leg are, namely the torque converter, the direction of rotation change gear and a disc of the mechanical Transmission, while only the other disk of the mechanical transmission is arranged on the other branch of the U.

Even if the transmission train is designed in a Z shape the inventive design of the power transmission s device a more compact design, since the direction of rotation change gear, the setting means of the directly from Torque converter driven pulley may overlap.

In an alternative arrangement using a uniaxial Transmission, e.g. a friction drive, the direction of rotation change gear itself can have two axes, whereby the possibility of forming a U-shaped or Z-shaped transfer train is given. A suitable one Friction drive is known as Beierreibantrieb and was developed by J.G. Giles in the book "Automatic and Fluid Transmissions" described by Odhams Press Limited, 1961, page 23 «

The direction of rotation change gearbox can have two selectively actuatable clutches and / or brakes that are used to

609827/0894

set the neutral position can be actuated, whereby the Output shaft separated from the drive and a forward and backward rotation of the output shaft can be effected. The change gear can for example be designed as a planetary gear, with the drive side with a sun gear and the output side are connected to a ring gear. Between sun gears and ring gears one can Coupling can be provided, which provides for the drive in the forward direction, while a brake for the drive in Backwards direction. When both the brake and the clutch are ineffective, the output side is off the drive side separated.

In an alternative embodiment, the direction of rotation change gear have a claw coupling, which is used to adjust the neutral division and thus to separate the output side can be operated from the drive side and to adjust the forward and reverse rotation of the output shaft. The direction of rotation change gear can a first shaft with rotatably mounted first and second gears that are driven by the dog clutch can be selectively coupled to the first shaft and have a second shaft forming the output shaft which a third and a fourth gear are attached, the first gear with the third gear and the second gear meshes with the fourth gear via an intermediate gear. On the first shaft can be one with external teeth provided sleeve be attached on which an internally toothed sleeve is mounted such that it can be displaced, that they are in a first position both with the sleeve and with external teeth on the first gear, in a second position with the sleeve and external teeth on the second gear and in a neutral position is not in engagement with either the first or the second gearwheel when the transmission train is interrupted, the claw coupling through the sleeve, the sleeve and

609827/0694

the external gears are formed.

The invention further comprises the combination of the above-described power transmission device and a drive machine, which drives the torque converter directly. In such a combination, in which the gearbox as Pulley transmission is formed, either the torque converter between the prime mover and a Pulley of the pulley drive or a disc of the pulley drive can be placed between the prime mover and the torque converter be arranged. The last-mentioned arrangement enables an even more compact design than the former arrangement.

Power transmission devices with the design according to the invention can be used particularly favorably in motor vehicles, wherein the prime mover is formed by the motor vehicle engine which is transverse to the longitudinal axis of the motor vehicle can be arranged. The power transmission device according to the invention can also be used advantageously, when the engine is arranged with the longitudinal crankshaft axis inclined about the crankshaft axis, the U-shaped transmission train favored a front-wheel drive very much.

The invention is explained in more detail below with reference to the exemplary embodiments shown in the drawing. In the drawing show:

Fig. 1 is a schematic representation of a power transmission device known execution;

FIGS. 2 and 3 are schematic representations of exemplary embodiments of the power transmission device according to FIG the invention;

FIGS. 4 and 5 cut or cut at right angles to one another. Partial sectional views of the schematically shown in Fig. 2 illustrated power transmission device;

6098 27/0694

6 shows a partial section through that in FIG. 3, schematically illustrated power transmission device;

Fig. 7 shows a section through an alternative embodiment of the direction of rotation change gear, which in the power transmission device according to the invention can be used;

8 shows a schematic view of a further exemplary embodiment the invention; and

9 and 10 are schematic representations of the inventive device Power transmission device when installed in a motor vehicle with a transverse engine.

Referring first to Fig. 1, there is shown a previously proposed arrangement in which a prime mover 10 drives a torque converter 11. The torque converter in turn drives a change gearbox 12, which drives a pulley of a continuously variable mechanical belt transmission 14. The other disk 15 of the Transmission 14 is connected to an output shaft 16 which drives a bevel gear 17 of a motor vehicle axle.

In Fig. 1 it can be seen that the transfer train from the Drive machine 10 to bevel gear 17 has a generally U-shaped arrangement and that three units, namely the Torque converter 11, the direction of rotation change gear 12 and the disc 13 in the upper leg of the U and only one Unit 15 are arranged in the lower leg of the U. The disadvantages described above result.

Fig. 2 shows an embodiment of the invention, and the corresponding parts in this figure have the same reference numerals as in Fig. 1 with the subscript a. From Fig. 2 is to recognize that prime mover 10a is directly driving torque converter 11a; the latter drives a pulley 13a of the transmission 14a. The direction of rotation change gear 12a is, however, from the second disk 15a of the gear 14a driven. The direction of rotation change gear 12a drives the Output or output shaft 16a and thus the If bevel gear 17a.

609827/0894

In this arrangement, two structural units are arranged in each leg of the U-shaped transfer train, namely the Torque converter 11a and the disk 13a in one leg and the disk 15a and the direction of rotation change gear 12a in the other leg. Compared to the embodiment according to FIG. 1, the arrangement according to FIG. 2 results in a smaller one Overall length.

Fig. 3 shows a second embodiment of the invention and corresponding parts in this figure bear the same Reference numerals as in Fig. 1 with the index b. In the exemplary embodiment according to FIG. 3, the drive machine 10b drives the torque converter 11b directly, but the disc 13b of the transmission 14b between the engine and the Torque converter, i.e. the drive goes through disk 13b to torque converter 11b and from there to disk 13b. The disk 15b drives the rotational direction change gear 12b as in the embodiment described above, and the output to the shaft 16b and the bevel gear 17b is derived from the direction of rotation change gear 12b. The order according to FIG. 3 enables an even more compact design than that according to FIG. 2.

The embodiment according to Figure 2 is below With reference to Figures 4 and 5 explained in more detail.

According to FIG. 4, the torque converter 11a has a on one Pump 18 attached to shaft 19. The shaft 19 is driven at 20 by the crankshaft of the prime mover 10a. A shaft 21 surrounds the shaft 19 and at its right end carries the non-displaceable part 22 of the disk 13a. Of the the other part 23 of the disk 13a is slidably mounted on the shaft 21. The disk part 23 has a cylinder portion 24, which receives a piston 25 fixed to the hollow shaft 21. A spring 26 is between the piston 25 and the movable part 23 effective and urges

609827/0694

the latter in Fig. 4 to the right. The hollow shaft 21 is supported by two bearings 27 and 28 arranged at a mutual distance stored in a housing 29.

The turbine or impeller 30 carries clutch disks 31 which are fastened to the shaft 21 on both sides Clutch disc 32 are arranged. A piston 33 is guided in a cylinder 34 formed in the hollow shaft 21 and can be shifted to the left in Fig. 4 to include the clutch disks 31 and 32 and thus the impeller to couple the shaft 21. The turbine or impeller also carries a coupling disk 35, which is in friction system with a surface 36 arranged on a component 37 can be brought. The component 37 connects by means of an in Piston 38 accommodated in a cylinder 39 of part 37, the pump wheel 18 with the shaft 19.

The reaction component of the torque converter is shown at 40 and via a one-way clutch 41 to the housing 29 connected.

The other disk 15a of the pulley drive 14a is shown in FIG. 5, the one relative to the sectional plane in FIG. 4 represents right-angled sectional view. This disk 15a is mounted on a hollow shaft 43 in a housing 42. The non-displaceable part of the disk is denoted by 44 and the displaceable part by 45. The immovable one Part is formed in one piece with the shaft 43, and the part 45 displaceable on the shaft 43 has internal teeth 46, which engages with external teeth on the shaft. The movable part 45 carries a component 47 in which a cylinder 48 is formed. In the cylinder 48, a piston 49 is received, which over a toothing is connected to the shaft 43. A spring 50 acts between the fixed piston 49 and the slidable one Part 45 of the disc and pushes the latter in Fig. 5

609827 / 0S94

To the right. A belt 51 made up of chain links Reaches into the space between the different and unvarnable Parts 45 and 44 of the disc 15a and between the fixed and movable parts 22 and 23 of the disc 13a a.

The hollow shaft 43 has an internal spline 52 which with a splined end portion 43 of a first shaft 54 in engagement. The first shaft 54 carries first and second spur gears 55 and 56. These spur gears are freely rotatable on the shaft 54 via bearings 57 and 58.

The spur gear 55 has an externally toothed shoulder 59, and the spur gear 56 has an external toothing provided approach 60. The shaft 54 has an external toothing provided section 61 of reduced diameter, on which one provided with internal teeth Sleeve 62, which also carries external teeth, is arranged. Outside on the sleeve 62 is one with internal teeth provided sleeve 63 is arranged. This sleeve 63 has an annular groove 64 into which an adjusting claw 64 'engages. if the sleeve 63 is in the position shown, the spur gears 55 and 56 are not connected to the shaft 54. The sleeve is in the neutral position, and it is to see that in this position the pulley gear 14a is separated from the second or output shaft 16a. If the sleeve 63 is shifted to the right in FIG. 5, so it connects the first spur gear 55 to the shaft 54, while when the sleeve 63 is shifted to the left in FIG. 5 a connection between the second spur gear 56 and the shaft 54 is established. The shaft 54 is via bearing 65 and 66 stored in a housing 67.

The output shaft 16a has a third gear 68 and a fourth gear 69. The third gear 68 meshes directly with the first gear 55. The fourth gear 69 meshes with an intermediate gear 70, which in turn with the second Gear 56 is engaged. It can be seen that the

B0 9827 / OS9A

Gears 55 and 68 rotate in opposite directions, while gears 56 and 69 because of the intermediate gear Turn 70 in the same direction.

The gear 69 meshes with a ring gear 17 a, which is on a Bevel gear differential 71 is attached. This bevel gear differential is of conventional design and drives two Half shafts 72 and 73, which are connected via constant speed connectors 74, 75 connected to the driven wheels of a motor vehicle, not shown in the drawing are.

The turbine wheel release clutch, which is held by the clutch plates 31 and 32, the piston 33 and the cylinder 34 is formed, is shown schematically at 76 with a Control device connected; The adjusting claw or fork 64 'is also connected to the control device 76.

Xm following, the operation of the embodiment according to FIGS. 4 and 5 will be described. The prime mover 10a drives the shaft 19, which in turn drives the impeller 18 of the torque converter. Assuming that the impeller clutch is actuated and the impeller locking clutch with the clutch disc 35 and the actuating piston 38 is disengaged, the shaft 21 is driven by the rotational movement of the impeller or turbine wheel caused by the impeller. The shaft 21 drives the pulley 13a, which in turn drives the pulley 15a via the chain belt 51. The transmission ratio, which is determined by the pulleys 13a, 15a and the position of the belt 51, is changed in a known manner by changing the effective radii of the pulleys 13a and 15a with relative movement of the respective moving parts of the pulleys with respect to the associated pistons. The output of the transmission is on the shaft 43 and the first shaft 54. A drive of the half-shafts 72 and 73 in one direction is caused by the

60982 7/0894

Sleeve 63 is shifted to the right, whereby the first Spur gear 55 is positively connected to shaft 54. The spur gear 55 drives the gear 68, which is via the gear 69 drives the ring gear 17a, the differential gear 51 and thus the half-waves. The drive of the half-waves in the opposite direction is achieved in that the sleeve 63 is shifted to the left, whereby the second Spur gear 56 is connected to shaft 54. The spur gear 56 drives the gear 69, and via the intermediate gear 70 this in turn drives the half-shafts 7 2 and 73 via the differential 71. The control device 76 is arranged in such a way that that with a planned reversal of direction the movement of the shift fork 64 with the actuation of the impeller release - clutch is synchronized, the torque converter being separated from the shaft 21, so the latter from the drive machine is separated. This arrangement prevents damage or accidental changes of direction at the in vehicles moving in one direction. If the sleeve 63 is in the position shown in FIG. 5, then there is the direction of rotation change gear in its neutral position, and the drive 14a is separated from the output shaft 16a. Therefore, if the motor vehicle is an emergency braking at high Transmission ratio of the transmission 14a takes place, the sleeve 63 can first of all before starting the motor vehicle brought into the neutral position and then the continuously variable transmission 14a to a low gear ratio be adjusted before the sleeve 63 to transmit a rotary movement in one direction or the other is shifted to the output shaft.

It can be seen that the transfer train has a U-shaped arrangement. That is, the transfer train goes from the Drive machine to the torque converter and from there to a disk of the continuously variable transmission 14a, wherein the torque converter and the one disc are arranged in one leg of the U. The drive train then runs over

609827/0694

the web part of the U, namely the chain belt 51 to the other leg of the U, which is through the other pulley and the Direction of rotation change gear is formed. The direction of rotation change gear is located under the torque converter or the prime mover. As a result, an extremely compact design is achieved.

FIG. 6 shows the exact design of the exemplary embodiment according to FIG. 3. The crankshaft of the drive machine 78 drives a shaft 79 which runs through the disc 13b to the torque converter 11b and with the impeller 80 of the torque converter connected is. The torque converter turbine or impeller 81 is via an impeller release clutch 82 is connected to a hollow shaft 83 to which the non-displaceable part of the disc 13b is attached. The other Part of the disk 13b is slidably mounted on the shaft 83. The more precise arrangement corresponds to that of FIG. 4 and does not require any further explanation.

A chain belt 86 runs on the two pulleys 13b and 15b. The disc 15b drives a shaft 87, which over Bearing 88 is mounted in a housing 89. This shaft carries first and second gears 90 and 91 similar to the first and second gears according to the embodiment Fig. 4, and one of these gears can be coupled to the shaft 87 via the dog clutch. The claw coupling has a sleeve 92 which is provided with an internal toothing and which is provided with serrated lugs 93 and 94 on the gears 90 and 91 can be brought into engagement. The gears 90 and 91 mesh with third and fourth gears, the in turn drive the differential and the two half-waves in accordance with the description of FIG. The order 6 can be made even more compact than that according to FIGS. 4 and 5 by the disk 13b of the continuously variable transmission is arranged between the drive machine and the torque converter (instead of

609827/089

the arrangement of the torque converter between the prime mover and the disk 13a in Fig. 4). The mode of operation of the exemplary game according to FIG. 6 corresponds exactly to that of the Ausführungsbexspiels according to Figures 4 and 5. Upon reaching the coupling point of the torque converter can the latter can be disengaged by actuating the locking clutch.

In the embodiments described above, there is a dog clutch with a spur gear for changing direction and setting the neutral position using. Instead, according to the invention, a planetary gear can also be used can be used to change direction. Such a planetary gear is shown in FIG. The transmission itself is designated by 12d, and the input shaft to the transmission is designated by 100. The input wave corresponds to the wave 54 in the embodiment according to FIG. 5 and is driven by the continuously variable transmission 14a, b of the power transmission device.

The shaft 100 is formed in one piece with a sun gear 101 of the planetary gear and has an axial Extension of an externally toothed cylindrical section

102 on. The planetary gear carrier 103 of the transmission carries a number of planetary gears 104, which with the sun gear 101 and a ring gear 105 mesh. The planet carrier

103 is assigned a band brake 106 which, when actuated, holds the planet carrier in place relative to the transmission housing. The ring gear 105 is connected to a cylindrical extension 107 which is provided with internal teeth. Interlocking Clutch disks 108 engage lugs 102 and 107 in two sets and form a clutch between the ring gear 105 and the sun gear 101. The clutch is via a piston 109, which is in a cylinder 110 is performed, hydraulically operated.

609827/0694

The output of the transmission forms a shaft 111, which via a flange 112 with the ring gear attachment 107 and with the Ring gear 105 is connected. The shaft 111 is in a blind bore 114 in the left end of the shaft 100 via a bearing 113 stored. The left end of the shaft 111 is mounted in a housing part 116 via a bearing 115. The shaft 111 has a bore 117, fed into the hydraulic medium can be, wherein a channel 118 is formed between the bore 117 and the cylinder 110, through the hydraulic medium can be supplied to the cylinder 110 for moving the piston 109 and for actuating the clutch 108.

When both the brake 106 and the clutch 108 are released, the shaft 111 is separated from the shaft 100, and the reversing gearbox is in its neutral position. When the brake 106 is applied, so the shaft 111 is rotated counter to the direction of rotation of the shaft 100, the clutch 108 being released. If the The clutch 108 is engaged and the brake 106 is released, the ring gear 105 is connected to the sun gear 101, and the shaft 111 rotates due to the direct drive in the same direction as the shaft 100. The actuation of the Brake 106 and clutch 108 is with the actuation of a wheel clutch in the torque converter as described synchronized in conjunction with Figures 4 and 5, so that the drive machine from the continuously variable mechanical transmission is disconnected when the direction of rotation change gear to reverse the direction of rotation of the Output shaft is adjusted.

The shaft 111 carries a spur gear 119 which drives a ring gear 120 connected to a differential gear. That Differential gear acts in the manner described in connection with FIG. 1 on an output shaft of a motor vehicle.

K 0 9 8 2 7/0 £ 9

Fig. 8 shows another embodiment of the invention, in which a friction drive of the above-mentioned Beier type is used, the output shaft of which is arranged coaxially to the input shaft. In Fig. 8, the same reference numerals are used as used in Fig. 1 with the index e. With this arrangement, however, the prime mover 10e is about a horizontal axis inclined or arranged at an angle. It drives the torque converter He, which is the friction drive 14e drives. The output shaft of the friction drive 14e is arranged coaxially with the input and forms the input shaft to the direction of rotation change gear 12e. This is arranged so that its output shaft 16e to one with Distance from the axis of the input shaft to the change gear 12e arranged axis rotates. The gearbox has similar to that previously described embodiments a neutral position. The output shaft 16e drives a bevel gear or a ring gear 17e. It can be seen that with this arrangement the output shaft 16e is returned under the drive motor 10e can be so that a compact design is created that still has a flat cover or hood line enables. Instead of an output shaft 16e emerging to the front, this can also be in the one indicated at 16f Way are guided backwards and drive a bevel gear or ring gear 17f. This enables a low hood line of a motor vehicle.

Figures 9 and 10 illustrate schematically the attachment of the power transmission device according to the invention a motor vehicle with a transverse engine. Fig. 9 is a schematic plan view with the front wheels of the Motor vehicle with 121 and the rear wheels with 122 are designated. The motor 123 lies transversely to the longitudinal axis of the Motor vehicle and drives a torque converter 124, which in turn is the input pulley 125 of a pulley drive as described above. Fig. 10 is a schematic front view showing that

6 0982 7/0694

the pulley 125 drives the driven pulley 126 via a chain belt 127. The output pulley drives via e ^ .n A reversing gearbox arranged in a housing 128, a differential gear likewise arranged in the housing 128 (Fig. 5). The differential gear acts on the front wheels 121 via constant speed links 129, which are also described in connection · / t FIG. It can be seen that this arrangement is very much compact and fits perfectly in a motor vehicle with a transverse engine.

Claims (11)

PATENTANWÄLTE ZENZ & HELBER · D 4300 ESSEN 1 · AM RUHRSTEIN 1 ■ TEL .: (O2 O1) 4126 87 Page - 18 - G 828 Expectations Q. ' Power transmission device with variable ratio, in which a hydrokinetic one driven by a prime mover torque converter and an output shaft or the like. intended are and a steplessly variable mechanical transmission and a selectively operable direction of rotation change gear in series between the torque converter and the output shaft are arranged thereby characterized in that the continuously variable mechanical transmission (14a; 14b; 14e) from the torque converter (11a; lib; lie) is driven directly and in turn the output shaft (16a; 16b; 16e, 16f) via the direction of rotation change gear (12a; 12b; 12e) drives and that the direction of rotation change gear has a neutral position in which the output shaft is separated from the continuously variable mechanical transmission is" 2. Power transmission device according to claim 1, wherein the A clutch device is assigned to the torque converter, which is used to interrupt the drive connection via the torque converter is selectively operable, characterized in that one of both the direction of rotation change gear (12a) as control device (76) assigned to the coupling device (31 ... 34) is also provided, which reverses the direction of rotation when actuated the output shaft (16a) via the direction of rotation change gear and at the same time by actuating the Coupling device an interruption of the drive connection causes on the torque converter (lla). z / bu. 609827/0694 3. Power transmission device according to claim 1 or 2, characterized characterized in that the variable mechanical transmission is a known pulley transmission (14a; 14b) is designed, in the case of dom βΊη belts or a chain {51; 86) runs over two disks (13a, 15a; 13b, 15b) rotatable on a parallel axis, the effective radii at least a rotatable disc for continuously changing the translation are changeable. 4. Power transmission device according to claim 3, wherein one of the parallel axes ait of the output shaft of the torque converter coincides and the transmission train of the power transmission device has a U- or Z-shaped course, thereby characterized that the torque converter (lla; lib) and a rotatable disc (13a; 13b) of the pulley transmission (14a; 14b) in one leg and the other rotatable disc (15a; 15b) of the pulley gear and the direction of rotation change gear (12a; 12b) are arranged in the other leg of the U- or Z-shaped transfer train. 5 «Power transmission device according to one of claims 1 to 4, characterized in that the direction of rotation change gear as a known three-component planetary gear (12d) is designed that a clutch (108) is arranged between two transmission components (101, 105) which causes an output in one direction of rotation when actuated, and that one acting on the third gear component (103) Brease (106) is provided which, when actuated, generates an output causes in the other direction of rotation. 6. Power transmission device according to one of claims 1 to 4, characterized in that the direction of rotation change gear (12a) has a dog clutch (59 ... 64) which is used for setting the neutral position, in which the output side of the drive side is separated, and the two directions of rotation of the output shaft (16a) can be actuated. B09827 / 0694 7. Power transmission device according to claim 6, characterized in that that the direction of rotation change gear (12a) has a first shaft (54) with the first shaft rotatably mounted thereon and second gears (55, 56) which can be selectively coupled to the first shaft via the dog clutch (59 ... 64), and a second shaft forming the output shaft (16a) on which a third (68) and a fourth (69) gearwheel are attached are, wherein the first gear (55) with the third gear (68) and the second gear (56) via an intermediate gear (70) with meshes with the fourth gear (69). 8. Power transmission device according to claim 7, characterized in that that on the first shaft (54) a sleeve (61) provided with external teeth is attached, on which an internally toothed Sleeve (63) is slidably mounted such that it is in a first position both with the sleeve (61) and with an external toothing (59) on the first gear (55), in a second position with the sleeve and an external toothing (60) on the second gear (56) and in a neutral division below Interruption of the transmission train is not in engagement with either the first or the second gear, and that the dog clutch is formed by the sleeve (61), the sleeve (63) and the external teeth (59, 60). 9. Power transmission device according to one of claims 3, 4, 6, 7 and 8 in combination with a torque converter direct driving engine, characterized in that the torque converter (lla) in a manner known per se Is arranged side by side between the drive machine (10a) and a pulley (13a) of the pulley drive (14a). 10. Power transmission device according to claim 9 in one Motor vehicle, characterized in that the drive machine (10a) is the motor vehicle engine and the output shaft (16a) drives two vehicle rudders via a differential (71). 60982 7/0694 " ²¹ " 25572A3 11. Power transmission device according to claim 10, characterized in that that it is attached in a manner known per se transversely to the longitudinal axis of the motor vehicle (Fig. 9, 10). 609827/0 6 94