DE20220391U1 - Infinitely variable transmission has a belt driven variable drive with flat belts fitted inside a planetary transmission - Google Patents

Abstract

An infinitely variable transmission with a compact layout and improved transfer efficiency has coaxial input and output shafts and a variable belt drive with crossed belts. The drive is positioned inside a planetary transmission and includes a switching clutch. The planet cage of the transmission serves as the flywheel of the whole system. To extend the effectiveness of the transmission it is coupled to two gear stages.

Description

[Utility model application]

[Name of the invention:] Device for continuous oreh conversion

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[Description]

The invention relates to a device for stepless mechanical rotation conversion, in particular for motor vehicles.

[State of the art]

It is known that ergonomic automatic transmissions, despite their uneconomical nature, are increasingly being used in vehicles around the world. Belt transmissions and toroidal transmissions are notable alternatives to known automatic transmissions. Due to the kinematic difference in the contact surfaces, such transmissions are preferably used with oil-lubricated friction metal pairs. However, this requires very high contact pressures and, as a result, high energy losses in the friction pairs, in the adjustable contact pressure devices and in the shaft ball bearings.

In addition, such transmissions require energy-intensive starting clutches and, in order to achieve the necessary speed adjustment of the output shaft, additional gear pairs, which results in higher energy losses, transmission weights, costs and larger dimensions. An increase in the nominal power of the drive also causes a disproportionate increase in the dimensions.

From the publication DE 100 21 912 A1, a transmission is known which replaces the starting clutch and creates a reverse gear in the toroidal transmission by means of an epicyclic gear. However, this transmission is too complicated, energy-intensive and cannot eliminate the other disadvantages of the toroidal transmission.

Furthermore, a transmission is known from the publication DE 31 31 169 A1 in which a forward movement, standstill and reverse movement of the output shaft can be adjusted and a direct torque transmission is provided in at least one transmission ratio.

Apart from the larger space requirement, the disadvantage of such a design of the mechanical transmission is that a direct torque transmission is kinematically impossible.

Finally, from the documents US 4 295 836 and DE 39 07 130 A1, transmissions are known in which flat and flexible belts are used between the pulleys of variable diameter, whereby essentially a pair of pulleys is stressed, which span a series of belt drive elements which are moved simultaneously both radially and in the circumferential direction.

Due to the impact of the polygon effect, the discreteness of the contact surfaces causes vibrations and energy losses. An attempt to compress the power by providing a guide roller within the extension of the pulleys causes additional energy losses.

The state of the art in continuously variable transmissions is therefore unsatisfactory. Continuously variable transmissions can obviously only be implemented if the efficiency, price-performance ratio and space requirements are on a par with those of a manual transmission and the ergonomics are comparable with those of an automatic transmission.

[Task of the invention]

The object of the invention is to provide a device for continuously variable mechanical rotary conversion, in which a high degree of efficiency and a good price-performance ratio are achieved with a small construction volume and simple operation like an automatic transmission.

The object of the invention is achieved with the features of the first protection claim. Advantageous further developments and embodiments are the subject of the subclaims.

To increase the efficiency and to expand the functions of a transmission, especially for motor vehicles, it is proposed that a torque from a drive shaft is transmitted to an output shaft either directly through a switchable clutch or via a rotary variator. The rotary variator consists of at least two pairs of rollers with variable diameters, which are connected in a closed loop by at least three flat and flexible traction means.

its snake shape is entwined crosswise and alternately on both sides.

The invention further comprises means for continuously changing the diameters of the rollers in pairs in such a way that different transmission ratios can be set.

Since the length of the traction means is constant and the same for each wrap, additional means are required to move the axes of the rollers.

In summary, this solution for the new rotary converter offers the following advantages:

- Dynamic closure - the contact pressures of the traction devices on the rollers are mutually compensated and not transferred to the axle bearings and control devices;

- kinematic differencelessness - kinematically caused energy losses are excluded in the friction pairs because cylindrical rollers and flat traction elements are used, whereby the energy losses due to buckling and slippage of the traction elements are low;

- Direct drive capability - over 70% of the driving time, torque is transmitted without energy loss because the rotary variator is only switched on when starting off and during strong acceleration;

- Starting clutchless - forward movement, standstill and reverse movement of the output shaft can be achieved smoothly and without a clutch;

- Controllability - adequate and precise control of the gear ratio and contact pressure is easy;

- Flywheel function - mass and space gain because the rotary variator can replace the flywheel of the combustion engine;

- Durability of the traction devices - service life and space saving because the traction devices are used on both sides and lengthways.

[Examples]

In the following, embodiments of the invention are explained and described in more detail with reference to drawings.

Fig. 1: a schematic longitudinal section through the rotary converter according to the invention,

Fig. 2: a section along the line A - A in Fig. 1 to illustrate the control device and the traction mechanism shape,

Fig. 3: a simplified top view of the rotary converter,

Fig. 4: a simplified perspective view of the variable diameter drive roller cut in two planes,

Fig. 5: a simplified perspective view of the drive roller cut in three planes with curved outer spokes and variable diameters,

Fig. 6(a, b): a schematic representation of the interaction of traction means and rollers with crank-shaped outer spoke axes,

Fig. 7: a schematic representation of the cone axis drive with return and double forward and

Fig. 8 is a schematic representation of a tracked vehicle drive with two rotary variators.

In the drawings, comparable components are marked with the same reference numbers.

According to Fig. 1, the rotary converter has a drive shaft 1 and an output shaft 2, which are arranged coaxially to one another. They can be connected to one another directly via a rotary variator with the rollers 26 and 27 or via a clutch 3. A sleeve 5 is rotatably and coaxially assigned to a planetary gear carrier 4 fastened to the drive shaft 1, so that outer guide disks 6, 7, which are removably fastened to the planetary carrier 4, and inner guide disks 8, 9, which are removably fastened to the sleeve 5, are arranged in pairs directly adjacent to one another.

Each of the guide disks 6, 8 and 7, 9 of an adjacent pair has two series of guides 10, 11 and 12, 13 in a curved parallelepiped shape. The adjacent guides 10, 11 or 12, 13 of a pair or of a guide disk 6, 8 or 7, 9 are arranged at an angle to one another in an anti-clockwise direction, so that the axes 16, 17 of the rollers 26, 27 are accommodated in end bushes 14, 15 which are designed in a curved rhombus shape in the spaces between the guides 10, 11 and 12, 13. This design can be seen better in Fig. 2 through the section AA.

Thus, a radial adjustment of the roller axes 16, 17 in alternately opposite directions can be achieved by generating a relative rotary movement between the guide disks 6, 8 and 7, 9. For this purpose, the inner guide disk 9 has a series of self-locking movement screw connections with a screw nut 18 and a screw bolt 19, which are actuated via gears 20, cams 21 and guide rollers 22, whereby the outer guide disk 7 has a toothed bean-shaped guide 23, so that when the screw bolts 19 are axially displaced, a relative rotary movement between the inner and outer guide disks 7, 9 and 6, 8 and a radial movement of the roller axes 16, 17 in opposite directions is generated.

The clutch 3 is driven by the cams 21 and hydraulic or pneumatic diaphragm cylinders 24 and 25.

The drive roller 26 and the driven roller 27 comprise, as shown in Fig. 3, a series of zigzag-shaped elastic lamellar rings 28, which are held together at their bends at a distance by tire-shaped tabs 29 to form tires.

Furthermore, a series of pivoting closed spokes 30, 31 (Fig. 2) are arranged, which have an expandable cross-section in the direction of rotation and connect the tires 28, 29 with those of the rollers 26, 27.

In order to make the surface of the rollers 26 and 27 stable and smooth, the number of spokes 30, 31 is maximized. Outer spoke pivot axes 34, 35 are inserted into holes 36 of the lamella bend rows and inner spoke pivot axes

axes 38, 39 are arranged in the hubs 32, 33, whereby, in order to keep the tires elastic, at least one row of sipe bends 37 is without bores or axles between two spoke pivot axes 34 and 35.

In order to maximize the number of spokes, according to Fig. 1 and Fig. 5, the spokes 30, 31 are arranged with an inclination to the roller axes 16, 17 and the tire tangents, wherein the spokes 30, 31 of all rollers 26, 27 are inclined in the direction of rotation of the drive roller 26.

The inner spoke pivot axes 38, 39 of the drive roller 26 are crank-shaped and are driven by teeth 40, 41 of a toothed bushing 42, whereby, in order to maximize the number of spokes, the cranks of adjacent spoke pivot axes 38, 39 or the teeth 40, 41 are axially offset. The toothed bushing 42 is connected to a threaded bolt 44 or to a gear 45 by an internal thread 43, so that the diameter of the roller 26 is changed when the threaded bolt 44 is axially displaced.

In the output roller 27, the hub 33 is firmly connected to the axle 16 or directly to the output shaft 2 by gears 46, 47, whereby the inner spoke pivot axes 48 are crankless.

As shown in Fig. 2 and Fig. 6, the drive rollers 26 and the output rollers 27 are wrapped crosswise and alternately on both sides by at least three flat, flexible traction means 49, 50, 51 in a closed snake shape, wherein the spokes 30, 31 have an inclination in the opposite direction of pull, so that the traction means 49, 50, 51 are tensioned depending on the output torque, or the traction is transmitted.

Fig. 6a shows a roller ratio of 1:1 and Fig. 6b a roller ratio of 1:2.

The planetary gears 45, 46 as well as the sun gear 47 and a hollow gear 54 provided with an inner groove 55 are enclosed by a hollow body 52 which is fastened to the guide disk 7 and forms an oil chamber 53 (Fig. 1).

The hollow gear 54 is connected by a freewheel clutch 56 to a non-rotatable bushing 58 which is axially displaceable in the slots 57 and which is supported by a

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Control force is applied depending on the driving condition and driving requirements. By axially displacing the bushing 58, the threaded bolts 44 and 19 also move axially, so that the diameters or the transmission ratios of the rollers 26, 27 are changed and the roller axes 16, 17 are alternately displaced radially in opposite directions, or the longitudinal difference required by the traction means is compensated.

According to the embodiment of Fig. 1, the diameters of the rollers 26, 27 and the gears 45, 46, 47 and 54 are selected such that in the extreme right position of the bushing 58 a standstill or even a reverse movement of the output shaft 2 can be set. In contrast, in the extreme left position of the bushing 58 the clutch 3 is actuated by the threaded bolt 19, cam 21 and the drive cylinders 24, 25 such that a direct drive is switched on, the hollow gear 54 being freed from the bushing 58 by the freewheel clutch 56 and the rollers 26 and 27 as well as the gears 45 and 46 being blocked.

Since an involute gearing is relatively insensitive to changes in the center distance, the gearing runs smoothly and it is sufficient if the number of rollers 26, 27 and the radial displacements of the roller axes 16, 17 are large enough or the changes in the center distance for the gear pairs 45, 54 and 46, 47 are relatively small.

If the number of rollers 26, 27 is too small, the planetary gears 45, 46 can be connected to the roller axes 16, 17 by means of cardan shafts or additional gear pairs. If the number of rollers 26, 27 is relatively large or the need for a smaller axis shift is small, the longitudinal difference in the traction means can be compensated for by an extension, or the roller axes 16, 17 can be arranged immovably on the planet carrier 4.

The longitudinal difference requirement of the traction means 49, 50, 51 can also be compensated by designing the crank-shaped outer spoke axes 61, 62 (Fig. 5, Fig. 6), so that the parts of the rollers 63, 64 wrapped around from the outside take up a larger diameter than the other parts when the common roller diameter is reduced, and a smaller diameter is achieved when the roller diameter is increased accordingly.

If a direct drive is not absolutely necessary, the clutch 3 and the freewheel clutch 56 can be dispensed with. In order to dispense with the clutch drive, the clutch 3 is replaced by a speed-effective, synchronously switchable or torque-switched clutch.

If necessary, the driven rollers 27 are equipped and operated with a motion screw hub like the drive rollers 26 to increase control reliability. To reduce stress, the motion screws 19, 44 and the bushing 58 are equipped with balls that move in thread grooves or slots 57. It is also possible that a material with a memory that can react to temperature, an electromagnetic field or other contactless control signals by changing its shape and/or volume is used for the slat rings 28, the tires or the entire rollers and/or as a drive for the spoke pivoting.

To increase service life and reliability, flat and smooth small link chains with rocker joint pins can be used as traction devices. If necessary, in order to make the tires of the rollers 26, 27 more elastic, the lamella rings 28 between the bends are designed to be T-shaped in cross-section. To ensure that the traction devices do not slip, the surfaces of the rollers 26, 27 are provided with grooves.

In order to keep a motor constantly connected to the output shaft 2, the freewheel clutch 56 is replaced by a clutch as required, which is operated synchronously in opposite connection with the clutch 3. In order to make the transmission more compact, the planetary gears 47 can be attached to the roller axles 17, the bushing 58 can be fixed in place and the screw bolts 19 and 44 can be operated or controlled by guide rollers from an additional guide sun gear via a groove.

If flat chains are used as traction means, the entire transmission is enclosed by the hollow body 52, which is either fixed to the guide pulley 6 or stationary, thereby forming an entire transmission oil chamber. If protection and cooling of the transmission is required, a protective cooling housing with air filter intake and air flap extraction is either fixed to the guide pulley 6 or stationary when belts are used as traction means, whereby the planetary gear

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carrier 4 is equipped with centrifugally arranged guide vanes and holes.

For a uniform utilization of the gear ratio range, the planet carrier 4 is fixed or designed to be rotatable via a clutch so that the sun or ring gears 47, 54 are fixed to the input shaft 1 or output shaft 2, whereby the motion screws 19, 44 can be actuated directly and a starting clutch can be used.

In a simple embodiment, the drive and driven rollers 26, 27 are fastened to the drive and driven shafts 1, 2 and wrapped in a known manner with a flat traction device, wherein the movement screw 44 is actuated directly by the control force.

When used in the automotive sector, the planet carrier 4 is removably attached as a flywheel to a crankshaft 59, shown in Fig. 3, of an internal combustion engine and the guide disk 6 is connected as a gear to a starter 60, whereby the engine-variator system is dynamically balanced.

In order to be able to fully use the direct drive when driving in town, off-road or on the motorway, the rotary converter, as shown in Fig.7 , is additionally equipped with at least two switchable gear stages, which, as well as a reverse gear, are combined with the axle drive, whereby, in the case of the hypoid axle drive, the drive bevel gears of double forward gears 65, 66 and a reverse gear 67 are arranged coaxially, switchably and on both sides of the output axle on a drive axle 70, in which an output bevel gear has two gear circles 68, 69. For an adjustable torque distribution, Fig.8, between chassis drive wheels 73, two rotary variators 71 with reducers 72 are arranged at the crankshaft ends 59, which is particularly important for tracked vehicles.

[List of reference symbols]

drive shaft 1 Output shaft 2 Clutch 3 Planetary gear carrier 4 Sleeve 5 Outer guide discs 6.7 Inner guide discs 8.9 Guides of the guide discs 10, 11, 12,13 End bushings 14,15 Roller axes
Screw nut 16,17
18 Screw bolts 19 Gears 20 cam 21 Guide rollers 22 bean-shaped guide 23 Hydro or pneumomembrane cylinder 24.25 Drive roller 26 Output roller 27 Lamellar rings 28 Tabs 29 Spokes 30,31 Roller hubs 32,33 Outer spoke pivots 34.35 drilling 36 Slat bending row 37 Inner spoke pivots 38.39 Teeth of the tooth socket 40.41 Tooth socket 42 Internal thread 43 Threaded bolt 44

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Planetary gears 45,46

Sun gear 47

Crankless inner spoke pivot axles 48

Flexible traction devices 49, 50,

Hollow body 52

Oil chamber 53

Hollow gear 54

Groove 55

Freewheel clutch 56

Slots 57

Socket 58

Crankshaft 59

Starter 60

Curved outer spoke axles 61,

Wrapping areas of the rollers 63,64

Drive bevel gears, advance gear 65,

Drive bevel gear return gear 67

Gear circles 68,69

Drive axle 70

Two rotary variators 71

Reductors 72

Chassis drive wheels 73

Claims (29)

1. Device for stepless rotation conversion with a drive shaft ( 1 ), an output shaft ( 2 ) and an intermediate belt variator with flat and flexible traction means, which has direct drive, standstill and return and can be switched mechanically or electromechanically, characterized in that - the drive shaft ( 1 ) and the output shaft ( 2 ) are arranged coaxially to each other, - the wrap-around variator is designed as a circulating variator and consists of rollers ( 26 , 27 ), of which at least two roller groups, designed in pairs as drive rollers ( 26 ) and driven rollers ( 27 ), are arranged planetarily and are wrapped by at least three flat flexible traction means ( 49 , 50 , 51 ) crosswise and on both sides in a meandering manner in a closed snake shape, - the planetary variator is arranged in a planetary gear, wherein the planetary gear carrier ( 4 ) is connected to the drive shaft ( 1 ), a sleeve ( 5 ) is coaxially and rotatably associated with the planetary gear carrier ( 4 ), the rollers ( 26 , 27 ) of the planetary variator are associated with the planetary gears ( 45 , 46 ), and the sun gear ( 47 ) is coaxially attached to the output shaft ( 2 ), - the outer surfaces of the rollers ( 26 , 27 ) of the rotary variator are designed in the form of zigzag-shaped lamellar rings ( 28 ), the diameter of which can be continuously varied by means of spokes ( 30 , 31 ) mounted on axes on both sides and inclined between the roller hubs ( 32 , 33 ) and the lamellar rings ( 28 ), - a clutch ( 3 ) is arranged between the drive shaft ( 1 ) and the output shaft ( 2 ), with which the torque can be transmitted to the output shaft ( 2 ) either directly or via the rotary variator and - the control of the displacement of the axes of the rollers ( 26 , 27 ) is carried out via guide disks ( 6 , 7 and 8 , 9 ) arranged in pairs and on both sides of the roller axes ( 16 , 17 ). 2. Device according to claim 1, characterized in that two outer, detachably attached guide disks ( 6 , 7 ) and two inner, detachably attached guide disks (8, 9 ) are arranged directly adjacent to one another on the planet carrier ( 4 ) and two inner, detachably attached guide disks ( 8 , 9) are arranged on the sleeve ( 5 ), each of the guide disks ( 6 , 7 and 8 , 9 ) having at least four guides ( 10 , 11 ) and ( 12 , 13 ) arranged diametrically and evenly in a curved parallelepiped shape, each guide ( 10 , 12 ) being arranged alternately to the adjacent guides ( 11 , 13 ) of a pair and to a guide disk ( 6 , 8 or 7 , 9 ) at an angle in the counterclockwise direction. 3. Device according to claim 1 and 2, characterized in that the roller axes ( 16 , 17 ) are arranged in at least eight bushings ( 14 , 15 ) which are designed in a curved rhombus shape and in the spaces between the opposite guides ( 10 , 11 ) and ( 12 , 13 ) of the adjacent guide disks ( 6 , 8 ) and ( 7 , 9 ). 4. Device according to claims 1 to 3, characterized in that at least two self-locking motion screw connections are arranged diametrically on the inner guide disk ( 9 ), which are each formed by a screw nut ( 18 ), a screw bolt ( 19 ) with cam ( 21 ), guide roller ( 22 ) and gear ( 20 ), wherein each motion screw connection is received in a toothed bean-shaped guide ( 23 ) of the outer guide disk ( 7 ), and a switching signal from the cams ( 21 ) can be transmitted hydraulically, pneumatically, mechanically or electromechanically to the switching clutch ( 3 ). 5. Device according to claim 1, characterized in that the lamella rings ( 28 ) are combined by tires, which are combined at intervals by tabs ( 29 ) at their bends and the spokes ( 30 , 31 ) are arranged in bend holes ( 36 ), with at least every second lamella bend row being free of holes, with their outer axes ( 34 , 35 ) pivotably such that the spokes ( 30 , 31 ) between the hubs ( 32 , 33 ) and the outer spoke axes ( 34 , 35 ) span surfaces with an inclination to the roller axis ( 16 , 17 ) and in the opposite direction of rotation, which have cross-sections that can be expanded in the direction of rotation, with the hubs ( 33 ) being coaxial and fixed to the gears ( 46 ) and by the sun gear ( 47 ) are rotatably connected to the output shaft ( 2 ). 6. Device according to claim 1, characterized in that at least two drive rollers ( 26 ), which differ from the driven rollers ( 27 ) in that they have spokes ( 30 ) with an inclination in the direction of rotation, the inner spoke pivot axes ( 38 , 39 ) being equipped with axially offset cranks and the bushings ( 42 ) being equipped with axially offset teeth ( 40 , 41 ) acting on the cranks of the spoke pivot axes ( 38 , 39 ) and an internal thread which forms a self-clamping movement screw connection with a threaded bolt ( 44 ), and the threaded bolts ( 44 ) are arranged in the hubs ( 32 ) in a rotationally fixed and axially displaceable manner and the gear wheels ( 45 ) are coaxially fastened to the threaded bolts ( 44 ) and connected to a hollow or sun gear ( 54 ). are. 7. Device according to claim 1 and 6, characterized in that the hollow or sun gear ( 54 ) is arranged with a toothing in a groove ( 55 ) and is connected by a freewheel clutch ( 56 ) to a non-rotatable bushing ( 58 ) which can be axially displaced by a control force. 8. Device according to claim 1, characterized in that an oil chamber ( 53 ) is formed by a rotating hollow body ( 52 ) which is coaxially fastened to the guide disk ( 7 ). 9. Device according to claim 1, characterized in that at least the axes of the planetary gears ( 46 ) are arranged immovably on the guide disk ( 9 ) and are connected to the output roller axes ( 16 ) by cardan shafts or by the gear pairs. 10. Device according to claim 1, characterized in that at least the roller axes ( 17 ) are arranged immovably on the planet carrier ( 4 ). 11. Device according to claim 1, characterized in that the outer axes of the spokes ( 30 , 31 ) are designed in the form of cranks ( 61 , 62 ) and the roller axes ( 16 , 17 ) are arranged immovably on the planet carrier ( 4 ). 12. Device according to claims 1 to 11, characterized in that the drive shaft ( 1 ) is not directly connected to the output shaft ( 2 ) and the ring gear or sun gear ( 54 ) is fastened to the bushing ( 58 ). 13. Device according to claims 1 to 12, characterized in that the clutch ( 3 ) is replaced by a speed-effective, synchronously switchable or torque-switched clutch. 14. Device according to claims 1 to 13, characterized in that the output rollers ( 27 ) are designed like the drive rollers ( 26 ), wherein the sun gear ( 47 ) is equipped with a groove and is axially displaceable by the actuation of the bushing ( 58 ). 15. Device according to claims 1 to 14, characterized in that at least one of the movement screws ( 19 , 44 ) and/or bushing ( 58 ) is equipped with balls migrating in thread grooves or in slots ( 57 ). 16. Device according to claims 1 to 14, characterized in that a material with a memory that reacts to temperature, electromagnetic fields or other contactless control signals by a change in shape and/or volume is used for the slat rings ( 28 ), tires or entire rollers and/or as a drive for the spoke pivoting. 17. Device according to claims 1 to 16, characterized in that flat and smooth small link chains with rocker joint pins are used as traction means. 18. Device according to claims 1 to 17, characterized in that the lamella rings ( 28 ) between the bends ( 37 ) are T-shaped in longitudinal axis section. 19. Device according to claims 1 to 18, characterized in that the surfaces of the rollers ( 26 , 27 ) are provided with grooves, the number of grooves corresponding to the number of traction means ( 49 , 50 , 51 ). 20. Device according to claims 1 to 19, characterized in that the ring gear or sun gear ( 54 ) is connected to the bushing ( 58 ) by a clutch. 21. Device according to claims 7 to 15 and 16 to 20, characterized in that the planetary gears ( 47 ) are fastened to the roller axes ( 17 ) and the bushing ( 58 ) is fixedly stationed, the screw bolts ( 19 ) and ( 44 ) being actuated or controlled by the guide rollers and a guide sun gear. 22. Device according to claim 17, characterized in that the hollow body ( 52 ) forms the entire transmission oil chamber and is either fixed on the guide disc ( 6 ) or stationary. 23. Device according to claims 1 to 16 and 18 to 21, characterized in that a protective cooling housing with air filter intake and air flap extraction is either attached to the guide disk ( 6 ) or fixed, wherein the planet carrier ( 4 ) is equipped with centrifugally arranged guide vanes and bores. 24. Device according to claims 1 to 19, characterized in that the planet carrier ( 4 ) is fixedly or rotatably stationed by the coupling and the sun gear ( 47 ) or hollow or sun gear ( 54 ) is fastened to the output or drive shafts ( 1 , 2 ), wherein the movement screws ( 44 , 19 ) can be actuated directly. 25. Device according to claims 1 to 19, characterized in that the drive and driven rollers ( 26 , 27 ) are fastened directly to the drive and driven shafts ( 1 , 2 ) and are wrapped around with a flat traction means in a known manner, wherein the movement screw ( 44 ) is directly actuated by a control force. 26. Device according to claims 1 to 23, in particular for motor vehicles, characterized in that the planet carrier ( 4 ) is removably attached to the crankshaft ( 59 ) of the internal combustion engine and the guide disk ( 6 ) is connected as a gear to a starter ( 60 ). 27. Device according to claim 26, characterized in that the rotary variator is supplemented with at least a two-stage and reversible gear, which is combined with the axle drive. 28. Device according to claim 27, characterized in that for a hypoid axle drive the drive bevel gears of two forward gears ( 62 , 63 ) and one return gear ( 64 ) on the drive axle ( 61 ) are coaxially switchable and arranged on both sides of the output axle, wherein the output bevel gear has two toothing circles ( 65 , 66 ). 29. Device according to claims 21, 27, characterized in that two rotary variators ( 71 ) with supplementary gears ( 72 ) are arranged at crankshaft ends ( 59 ).