DE8108351U1 - Additional variable speed gear for power controllable drive machines - Google Patents

Description

State of the art

The invention relates to an additional control gear for a power-controllable drive machine, which over a wide Speed range should bring a constant power output. Particularly in the case of cutting machines, a constant Power output required to ideally keep the chip cross-section and cutting speed the same for every turning diameter to be able to.

The status of the relevant development can be seen in the overview article "Drives for machine tools, 1. Main drives for cutting machine tools "of the magazine" Der Konstrukteur ", No. 7 - 8/1980, pages 46 to 49, in the publishing house for technology and economy, Meynen KG, Wiesbaden. According to this overview, it is generally known that the design limited range of power controllable prime movers - Preferably electric control motors -, in which this according to their throttle curves at the different speeds depending on the application (e.g. turning workpiece) still result in the same output torques (e.g. for maximum cutting depths), to be expanded by placing between the motor and the actual reduction gear still arranges one or more additional variable speed gears in the machine tool. These should be in the adjacent areas only compensate mechanically for the additional drop in speed of the motor in the direction of constant power output,

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However, the main area of application of the machine is direct drive the engine speed to the actual main gearbox, deis reduced to the final speed depending on requirements.

The constant power output is then coordinated specifically to the control characteristics of the drive machine Additional control gear between a power-adjustable drive unit and one located in the machine tool Main gear as well as by means of this upstream continuously variable additional control gear and finally also with combinations achieved by both types of intermediate translation. The most effective power control is achieved with motors which can be easily controlled or regulated and their speed, for example, via tacho generators, potentiometers etc. is sensitively adjustable and in which the associated additional control gear depending on the speed range can be operated automatically under load. With combinations of continuously variable and high-speed manual transmissions the most sustainable way to overcome the limited adjustment range of the former.

The additional variable-speed gears are accommodated in particular in the case of machine tools for heat dissipation and maintenance reasons outside the main gearbox in a separate housing. This way of setting up can also be seen, for example, from the SIEMENS catalog DA 35.1981, order number E 860 10-K 4G35-A 100-A 1, Section 5, on pages 1 to 12. The

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Asked accommodation of the additional variable speed gearboxes in separate housings with drives and drives configured as a belt drive and external actuators for switching actuation has long since proven itself on a broad basis, but is with regard to manufacturing and assembly costs, the risk of damage and accidents, as well as space requirements and ease of maintenance and energy use can still be improved:

First of all, the motor bearing on the output side is due to its additional load from considerable lateral forces the output is heavily stressed on one side, so that special precautions and monitoring are required, in order to achieve sufficient lifetimes. Furthermore, the use of belt drives worsens also the efficiency and operational reliability.

The increased requirements in terms of power size and switching accuracy of modern machine tools In addition, there are adjustment problems with those that are arranged individually on separate consoles and with the local ones Actuators to be individually adapted to the available space are also no longer economically and reliably manageable.

In the case of particularly precise drives, it is also annoying that as a result of switching shocks such. B. by changing the Direction of rotation or through rapid changes in the speeds, the elasticity of the belt drives or the slip occurring there the most diverse func-

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tion errors in the driven machine or its control or impairment of its work results can evoke.

The resolved design of the previous arrangement also led to accommodation problems due to the large amount of space required for the actuators to operate the additional variable speed gearbox. Individual consoles and struts were necessary. The belt drives required space-consuming protective grids.

The spaces between the individual units and protective grids also resulted in dirty corners on the entire system in which chips etc. got caught, and a reliable corrosion protection became significant in such nooks and crannies difficult.

The provision of differently designed engine mounts for applications with and without an additional variable speed gearbox was costly.

The object of the invention was therefore to provide an additional control gear for variable-speed drive-based machines with constant To create power output over a wide speed range, in which a more advantageous manufacturing and Assemblability with improvement of the efficiency, the life expectancy and the ease of maintenance as well the use of space without additional heating effects on the main transmission or the actual machine tool can be achieved, - and the retrofitting is more appropriate Drive machines (motors) do not raise bearing reinforcement problems.

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This task is defined by the one in the characterizing part of the claim invention illustrated solved.

With this arrangement according to the invention, the following are made

Benefits achieved:

- The engine output speed is fed into the additional variable speed gearbox without slipping and without any loss of efficiency. Waste heat does not radiate in an uncontrolled manner, but is m. By the engine cooling system in front of the machine tool

discharged.

The additional variable speed gearbox can, thanks to its special design | processing now with the highest possible input speed «· work, i.e. build very small and react more sensitively. The previously common speed reduction using a belt transmission is not required. This also improves the efficiency of the power transmission. The storage of the drive motor is now completely relieved of side forces from the belt output and can can be used at any time unamplified or only with normal maintenance.

The installation space for the belt drive, its protective grille and the weights of the belt pulleys and the separate Console for the additional variable speed gearbox is omitted. The assembly of the additional variable speed gearbox and the prime mover It also reduces the risk of accidents and damage, especially since the transmission is now is arranged less exposed.

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The assembly and adjustment of the additional variable speed gearbox is now very simple and already complete during the fabrication together with the actual drive machine possible. On-site adjustments and adaptation work omitted.

The more precise and more rigid drive connection by eliminating at least one belt drive improves the control and Work results in particular by reducing vibrations and reducing the centrifugal masses. in the The range of normal drive loads is an almost loss-free direct drive with a ratio of 1: 1 possible.

, - The entire machine is clearly structured by

the control drive is now combined "in one piece". There are also no unsightly dirty corners and edges. The merging of the housing parts of the drive machine and additional control gear and the derivation of the output side forces on a common foundation by means of the

concentric flange connection saves extensive

Console constructions and associated assembly methods

work.

si - The inclusion of the actuators in the housing opens up

further assembly and operating advantages.

- The use of the common housing for axial and

radial fixing of the output shaft and bearing or shaft connection to the drive machine not only saves

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the usual first belt drive, but also a reinforcement of the motor-side drive bearing and results in a dual use of the gearbox bearing that

it makes it possible to use very small output gears. The resulting increased tensile forces

• | (Centrifugal effect) can over this bearing or the

- ■ Housing lighter than the already stable engine foundation

can be derived than with a separate console. The motor

[;, weight already opposes the tensile forces, so

/ | that the anchoring is not significantly strengthened

needs.

- With the relocation of the additional variable speed gearbox to the engine, the heat generated there is also easier Wise discharged and kept away from the main engine to be driven. Also in terms of noise reduction advantages.

Advantageous further developments of the invention are contained in the claims:

- With claim 2 it is achieved that the output shaft can be substantially stiffened by a hollow shaft and that the most heavily loaded bearing comes from the driven gear is easily accessible.

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With claim 3 it is achieved that the assemblies of the Additional variable speed gearbox can be combined with one another in such a way that in those cases in which no speed converter is necessary, but the same reinforced bearing can be assigned to the drive machine can, which is used in cases of need with an additional variable speed gearbox.

According to claim 4 it is achieved that the actuators of the After it has been switched off, the speed converter automatically returns to a starting position in which the power control the prime mover alone is effective.

According to claim 5 it is achieved that the actuators can also be actuated when the machine is working, and that the map area for constant output power from the drive machine is as seamless as possible and adds without a jump in speed.

According to claim 6 it is achieved that the space required for the hydraulic actuators is extremely small and whose actuating force is directly transferrable. In addition, the oil supply in the housing can also be used as a lubricating oil sump to be used.

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According to claim 7 it is achieved that the additional control gear with high efficiency and high power transmission capacity is working.

According to claim 8 it is achieved that the additional control gear is very compact and works in an energy-saving manner and that its outer contours adapt favorably to those of the prime mover.

According to claim 9 it is achieved that the additional control gear is uninterrupted on the extended map range is switchable.

According to claim 10 it is achieved that the available friction surfaces of the additional control gear instead of one separate motor brake for locking the output shaft without running on when the drive unit is switched off become usable.

According to claim 11 it is achieved that the adaptation of the map while the speed converter is switched on and is possible without switching jumps in a particularly favorable way with a large bandwidth.

According to claim 12 it is achieved that the advantages of simplicity of a constant transmission epicyclic gear with a stepless variable speed gearbox together an even larger area of application for the main machine to be driven results than is possible with one of the gears alone.

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With claim 13 it is achieved that any drive motor can be used, as this one continuously variable power maintenance is assigned.

According to claim 14 it is achieved that the drive machine is a motor with constant electrical power can be, in which the main area of application is a direct drive through the additional variable speed gearbox he follows.

According to claim 15 it is achieved that the epicyclic gear is designed in a particularly proven and production-favorable manner.

According to claim 16 it is achieved that the shaft connection as a further axial definition also on the Helical teeth to be traced back axial forces can be designed accordingly.

According to claim 17 it is achieved that the drive connection between the continuously variable transmission and the epicyclic gear can be designed in a particularly space-saving manner.

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The invention is illustrated in the following with the aid of a schematic Drawings explained in more detail.

Fig. La shows the basic structure of the arrangement according to the invention with a two-stage Epicyclic gearbox,

Fig. Ib shows the reinforced with the applied Bearing shield possible use of the latter without additional variable speed gearbox with direct flange mounting on the drive machine.

Fig. 2 shows the basic arrangement of an

prime mover, which is directly followed by a variable-speed, continuously variable transmission is, while the additional control gear to complement the power constant this is flanged.

Fig. 3 shows a section through the additional variable speed gearbox in countershaft design with form-locking clutches.

Fig. 4 shows a section through the additional control gear in epicyclic gear design according to a preferred embodiment with power switchable Hydraulic couplings.

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The so far most common equipment of the prime mover ^ with additional variable speed gears that prevent changing heat influences on the machine to be driven are separately upstream, led because of the previously necessary considerable expenditure on components and power losses to several disadvantages.

- The installation space to be created independently of the housing of the motor with anchoring, adjustability, etc. for the additional variable speed gearbox required a first of its own there Drive connection from the bearing or the shaft of the drive machine and the journal ran out. In practice, only a first belt connection came into question, and that too had to run with the frequently occurring 1: 1 switching, so then caused unnecessary additional losses. Practically from case to case with the usual design Changing mounting or accessibility requirements also made the speed converter extremely variable Arrangement or design of the actuators necessary. The individual adaptation and the associated variable arrangement outside a common housing was therefore seen as essential. Occasional attempts an integration of the additional variable speed gearbox into the main

Shoots have not been satisfactory because of the local heat concentration.

With the second drive connection to the main gearbox from the separately installed additional variable speed gearbox, the entire drive train considerable flexibility and sales 5751 F

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Susceptibility to wear and tear. In addition to very careful assembly, increased maintenance was required. Also let themselves be this arrangement even with automatic control speed or. Do not always reliably avoid jumps in pulling force. It it is often important that the transition from one control range to the other is smooth and smooth, so that Frequent switching back and forth between the control ranges, for example triggered by signals from a tachometer generator avoided on the actual chuck in the main machine for the purpose of consistent work results will.

The one in Pig. ¹ 1a, the direct connection according to the invention of the additional variable-speed transmission 2 to the drive machine 1, which is already visually obvious, leads to considerable simplifications. A bell housing 9, which can always be manufactured to match a corresponding housing 4 of the prime mover 1 regardless of the application, now also carries the complete additional gear 2 independently, without its own foundation, under supervision of assembly problems, in which the actuators 12 can be installed from the start due to the fact that accessibility is always the same are. The shaft connection 11, which replaces the first belt drive of the previous design, can be made torsionally rigid and slip-free, so that with a constant gear ratio between the drive machine and the second belt drive 19 there is practically no loss of efficiency at this point or any wear processes

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would expire. According to the invention, straight and from the The drive machine 1 is independently particularly powerfully designed bearing 15 for the speed converter 10 and the output shaft 13 is located on the well-coolable engine facing away Side of the additional control gear 2, and this is spatially completely separated from the main gear 3.

Fig. Ib shows the possibility that with the housing cover 45 or bearing neck 16 provided bearing assembly of the additional variable speed transmission according to the invention even without this only to be used to reinforce the motor shaft bearings and only when needed. Performance indicator area to be combined with a corresponding speed converter.

Fig. 2. shows a further expansion option, which one of them it is assumed that a non-adjustable drive unit with a variable-power, continuously variable mechanical transmission

same
is operated in / direction. The speed converter 10 is installed directly on the drive machine 1 in a correspondingly larger bell housing 9 in a similar manner, as in the arrangement according to FIG. 2a. The output wheel 14 of the continuously variable feed gear 46, designed as a belt vario drive, for example, engages with the first external clutch driver 22 of the mechanical step speed converter (according to FIG. 1 a) via an intermediate wheel 47 rotating on the same shaft. at

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this combination has a circumferential toothing on and is rotatable with respect to the shaft journal 7 of the drive machine 1, because this is now the drive wheel of the stepless gearbox 46 has to take with you.

_v This design not only has all the structural advantages of the

in front of the described design, but offers thanks to the

- Continuous power maintenance with a corresponding Control system R the possibility of the electrical control range for motor 1 with this stepless preliminary stage

to replace. The use of normal motors without electric This makes power control possible.

It is a further advantage that the actuators also in this combination in the same housing 9 are closely grouped and can be accommodated in a protected manner.

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A design option related to the basic principle according to FIG. La shows the embodiment according to Figure 3 · A preferably electrically controllable drive machine J 'is an additional variable speed gear designed as a countershaft gear 2 assigned. Both are spatially separated from a main gear 3, mainly for reasons of warming.

In the housing 4 of the drive machine 1 (motor) its bearing 5 carries the shaft 6, of which a shaft journal 7 is on the output side protrudes so far that it is within the flange connection 8 of the bell housing 9 of the additional control gear 2 with the speed converter 10 located therein is arbitrary

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Design via the shaft connection 11 when assembled in a form connection can be brought. The actuators 12 acting on the speed converter 10 or the switching elements connected therewith enable the change in the speeds of the output shafts with the output wheel 14 attached to it, the bearing 15 thereof is held in a protruding from the bell housing 9 bearing neck 16 according to the invention so that the output gear 14 in the essential around him. Thus, the output gear 14 hardly requires any additional length or only a bending force caused at camp 15. The bearing 15 or the bell housing 9 of the additional variable speed gearbox 2 carrying it is therefore inustande, also absorb the bearing forces from the speed converter 10 and effectively relieve the drive machine bearing 5. the Output shaft 13 ends in the example shown with the output gear 14, which both axially and radially opposite the Storage 15 is set in the bearing neck 16, which it encloses tightly on the circumference.

In the embodiment of the speed converter 10 shown here as a countershaft transmission of a type known per se, which is also well suited for high torques

therefore, a complete assembly, independent of the prime mover 1, can be realized. In the installation position the additional variable speed gearbox therefore only from the prime mover 1; carried and held together by means of the flange connection 8 with her. The exact axial alignment to the shaft 6 of the drive machine 1 is therefore without its own consoles or foundations always guaranteed.

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The drive connection from the prime mover 1 (motor) to

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Speed converter 10 (countershaft transmission) takes place according to this example (Fig. 3) slip-free and torsionally rigid at the shortest distance via a shaft connection 11 that keeps the motor-side shaft journal 7 and a first gear Zl rotating on the output shaft 13 concentric to it in the operating state.

On the one hand, the gear Zl is in engagement with one that is mounted in the bell housing 9 parallel to the output shaft 13 Countershaft V or the two gearwheels Z2 and Z3 mounted on it. On the other hand, the gear Zl has another one On the output side shift ring gear ZKl, which in a manner known per se has a fixed on the output shaft 13 Muff carrier M and a shift sleeve SM which is axially displaceable thereon is assigned.

The sleeve carrier M or the output shaft 13 fixedly connected to it either to the gear Zl or to one, the socket carrier M, on the output side downstream, to the output shaft 13 coaxial gear Z4, be switched on. This gear Z4 is rotatably mounted to the output shaft 13 in the housing cover 45 and has Also a gear ring ZK4 on the sleeve carrier side. If this is in engagement with the sleeve carrier M, the Translation from the countershaft V. If it is disengaged and is the sleeve carrier M with the gear rim ZKl |

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connected, the transmission from the countershaft V is switched off and the additional control gear 2 has input speed ~ output speed. By placing the gear Z4 directly radially above the bearing 15 of the output shaft 13 on an inner support collar of the bearing neck 16 that is integral with the housing bell 9 and the output wheel 14 closely enclosing it on the outside, a short overall length of the entire additional variable speed gearbox 2 is achieved. As a result, a problem-free direct connection of the bell housing 9 of the additional variable speed gear 2 and the motor housing 4 via the precisely fixing flange connection 8 is possible without the need for separate foundations or brackets or the bending forces from the output gear 14 hindering or. would assume disadvantageous dimensions.

An even more compact design of the additional variable-speed transmission 2 according to the invention results from the design of the speed converter 10 as a planetary gear according to FIG. 4, as is also shown in the principle drawing, FIG. Here, too, the basic principle already outlined in the explanation of FIG. 3 is the arrangement of bearings and Switching elements realized.

The output shaft 13 ends in this example with a hollow shaft 17, which is both the axial and the radial Fixed with respect to the bearing 15 guaranteed and their internal drivers (18) (z. B. spline) and axial collar distances etc. are preferably dimensioned so that they are also on

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the shaft journal 7 of the drive machine 1 can be pushed over directly are, if once (according to the basic principle of Fig. Ib).

a storage 15 without an upstream speed converter 10 to avoid excessive stresses on the bearing 5 of the The drive machine 1 is attached to this directly via a flange connection 8 of the same type, as with the speed converter 10 shall be. In this case, the bell housing 9 would, of course, only be necessary in a short design. Im shown here For example, an epicyclic gear 20, known per se, is provided that fits the outer contours of the motor well adapts and is also well suited for high speeds. Although it is designed to be a complete assembly independently

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can be done by the prime mover 1, but it is in

\ Installation position of this alone by means of the flange connection 8

carried and held together. So there is no need for separate consoles or foundations and the exact axial alignment to the shaft 6 of the drive machine 1 is always guaranteed. The drive connection from the prime mover 1 to the speed converter 10 takes place in a slip-free or torsionally rigid manner via the shaft connection 11, which is interlocking with the shaft journal 7, which is designed here as a hub 21 of a first clutch external driver. This has one with the hub 21 Outer ring 24 forming ring cylinder 23, in which a first ring piston 25 against an axially acting return spring 26 longitudinally movable against a friction connection 27 held half in the outer ring by means of pressure medium in the ring cylinder 23 can be pressed downstream. The pressure medium supply 28

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to the annular cylinder space 23 takes place via bores or channels 29 in the hub 21 or a slip ring 30 rotatably mounted on it from the wall of the bell housing 9. The second half of the first friction connection 27 is held by a first clutch inner driver 31, which rotates with a planetary gear support ring 32 held non-rotatably on the output shaft 13 - the pin 34 carrying planetary gears 33 is connected to an outer central gear 35. Planet gears 33 are on the one hand in constant simultaneous tooth engagement with a pinion 36 (sun gear) held in a rotationally fixed manner in the hub 21, but which is held in a rotationally movable manner with respect to the output shaft 13 and preferably on a central bearing 37 fixed radially and axially to this in addition to the support effect by the externally engaging it Planet gears 33 is performed again. On the other hand, the planetary gears 33 are again in engagement on the outside with a ring gear 38 comprising them and the central gear 35 on the outside from the output side, which has a second outer clutch on its circumference. \ driver 39, via which a second friction connection 49, M, which is rotatably held by a second clutch outer driver 41 to the 1 bell housing 9, by means of a | second ring cylinder 42 and second ring piston 43 as a brake of the ring gear 38 can be switched on. Output side from:

ring cylinder 42 fixed to the housing and in front of one on the outer end face The bearing cover 44 flanged to the bearing neck 16 is both the output shaft 13 and that of it

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cantilevered hollow shaft 17 supporting bearing 15 arranged, which is exposed to the output side forces. These Storage 15 is dimensioned according to the invention so that it if necessary as an independent assembly together with a corresponding housing cover 45 also directly the drive machine 1 can be flange-mounted, where it is to be used without an additional variable-speed gearbox 2.

The mode of operation of the additional control gear according to the invention basically corresponds to the type known from the prior art;

In a predeterminable range of mostly common speeds (e.g. approximately η = 1000 to 4000), a stepless one works Control (either the electrical motor control or a mechanical additional switching stage corresponding to this, if no Control motor is available) with the constant ratio built into the drive train (e.g. 1: 1). For this purpose, the drive connection established via the second friction connection 40 with block circulation of the entire transmission is without additional losses in the direct drive through the power available at the first clutch outer driver 22 are provided. This can be done in a manner known per se in the entire area by means of a corresponding controller R 1. the on the actuators 12 acts in the direction of speed drop compensation, | be kept constant.

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But then (ζ. Β. Because of harder materials, larger Workpiece diameters or the like) are worked with a lower spindle speed, the output would be Performance at important speeds that are still required relatively often (e.g. between η = 250 to 1000) to unusable Values have fallen. Therefore, the additional control gear is now switched on (e.g. at η = 1000). If its translation i = 4, the range of constant output power also shifts by a quarter each, so in is then the desired speed range also P = constant and the change in the speed drop is in the same ratio as with 1: 1 ratio proportional to the change in diameter, etc. - Based on the arrangement shown here this means that the additional variable speed gearbox must be activated at least shortly after the engine has been switched on. To do this is the first Friction connection 27 is opened and the second 40 is closed, the sun gear 36 is no longer blocked by the Planet gears 33 held, but it rolls with the same in support against the ring gear 38 while driving of the central wheel 35 or the output shaft 13 with a corresponding translation in the same direction of rotation. It will ever after translation of the planetary gears 33, the drive speed for the main transmission 3 is more or less slow than itself the engine speed changed. The point is finally reached where the available power drops again begins (e.g. η approx. 1000), gear 2 is switched off,

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in that the first friction connection 27 is closed and the second friction connection 40 is opened, whereby the hollow wheel 38 is thus f can run free. Thereby the power flow over the first

Friction connection to the drive shaft 13 is established directly, and the clutch 22 rotates rigidly with the planetary drive, while the stepless upstream of this switching step

f Control now in the higher speed range (e.g. η = approx. 1000

up to 4000) keeps the power constant.

) |. The configuration according to the invention is a matter of course

electrical and

with both pressure-controlled and / electromagnetic

f actuators and various types of transmission systems can be implemented. The design described above, however, has the advantage of greater smoothness and compactness with good

ti precision and particularly low maintenance requirements.

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Claims (17)

·., A $ 4O8 3SW.s j ;; - ■: · ·; · | . ..... ZAHNRADFABRIK f'rIEDRICHSBAFEN ·· ': Aktiengesellschaft Friedrichshafen additional variable speed gear for power controllable drive machines - & r- & M. claims 1. Additional variable speed gearbox (2) for power-adjustable drive machines (1) essentially consisting of: a speed converter (11) in the drive train between a power controllable drive machine (1) and. a main gear or actuator (3), - which is the increase in the drop in speed when the power drops outside the economic control range the drive machine (1), if necessary, largely in the direction of constant power output to the main transmission (3) compensated, - A housing (9) for the installation of the speed converter (10) with the output shaft (13) mounted therein and a driven gear (14) or pulley rotating with this with a drive connection (19) to the main transmission (3), - as well as the control devices and actuators required to operate the additional variable speed gearbox (2), characterized, File 5751 F 07.HU ¹ J A. ^l JÜ \. 'Z ^: .!. • a o · <· F mi a) that the additional control gear (2) or the speed converter (10) via a power-adjustable drive (1) directly downstream releasable shaft connection (11) can be driven in a torsionally rigid manner,> b) that the housing (9) has a flange connection (8) which is concentric to the drive (1) and a protruding one Bearing neck (16) on the output side is designed as a cantilevered housing bell (9), which the speed., converter (10) and actuators (12) as well as a shaft connection (11) together and these together with the output shaft (13) and its bearing (15) axially and radially. 2. Zusatzregelgetrxebe according to claim 1, characterized, that the output shaft (13) with a hollow shaft (17) guided in the bearing (15) of the bearing neck (16) via an internal driver (18) of the same is drivingly connected, and that the bearing neck at its free end (16) of the housing bell (9) on the outside tightly enclosing υ output gear (14) is arranged non-rotatably. 3. Additional control gear according to claim 2, J5j characterized by - That bearing neck (16) and hollow shaft (17) dimensions have, which correspond to the gear-side part of the shaft connection (11). File 5751 F 4. Additional control gear according to one of claims 1 to 3, characterized in that the actuators (12) of the speed converter (10) have a starting position with constant transmission. 5. Additional control gear according to one of claims 1 to 4, characterized in that that the actuators (12) are hxlfskraftbetatxgbar and from by means of the control device of the power regulating unit ren drive machine (1) during operation, avoiding power interruptions or speed jumps consist of clutch pressure plates that can be brought into contact. 6. Additional control gear according to one of claims 1 to 5, characterized in that that the actuators (12) hydraulic cylinders (23, 42) and their pressure medium is also the lubricant of the speed converter (10). 7 »Additional control gear according to one of claims 1 to 6, characterized in that the speed converter (10) is a countershaft transmission, which can be switched in one or more stages by means of clutches (22, 3, 9). File 5751 F ·· ■ »II 8. Additional control gear according to one of claims 1 to 6, characterized in that that the speed converter (10) is an epicyclic gearbox which has one or more stages by means of clutches (22, 3, 9) is switchable. 9. Additional control gear according to one of claims 1 to 8, characterized in that that the clutches (22, 3, 9) can be switched under load. 10. Additional control gear according to one of claims 1 to 9, characterized, - That by means of the clutches or brakes (22, 39) also the drive machine (1) continues to run when it is switched off is preventable. 11. Additional control gear according to one of claims 1 to 10, characterized, - That the speed converter (10) is a continuously variable upstream gearbox (46), which is operated by means of pulley adjustment devices is variable. 12. Additional control gear according to one of claims 1 to or 8 to 10, characterized in that the speed converter (10) is a combination of an epicyclic gear with a continuously variable transmission. File 5751 F t t f> 13. Additional control gear according to one of claims 1 to 12, characterized in that that the drive machine (1) is a motor with a continuously variable transmission regulated in the direction of constant power. 14. Additional control gear according to one of claims 1 to 13, characterized in that that the prime mover (1) is a motor with constant electrical power control. 15. Additional control gear according to one or more of claims 8 to 14, characterized in that the epicyclic gear consists essentially of: a) a first external clutch driver (22) rotating with the output shaft of the drive machine (1), between its hub (21) and outer ring (24) a first annular piston (25) guided axially movable against springs is which, when pressure medium is supplied, a first friction connection (27) carried along by its outer ring (24) activated, the clutch inner driver (31) with a planet gear support ring (32) are in engagement; b) one with the planetary gear support ring (32) via planetary gears (33) bearing bolts (34) connected to the outer central gear (35), the ring gear (38) surrounding it on the outside * File 5751 F • it · · · t ft · ■ I I · ···· «» Bi « is axially fixed, which with a motor-side Internal toothing with the planetary gears (33) and with an external toothing on the bearing side with friction bodies a second clutch outer driver (39) is in engagement, between the hub and outer ring of a second Ring piston (43) is guided axially movable against springs, which when pressure medium is supplied against one of his the second friction connection (40) (brake) held on the housing (9) fixed on the outer ring comes to rest; c) and a pinion (3.6) supported between the shaft of the drive machine (1) and the outer central wheel (35) (Sun gear), the drive side with the shaft and on the output side in engagement with the planet gears (33) stands. 16. Additional control gear according to one of claims 1 to 15, characterized in that - That the detachable shaft connection (11) consists of one with the output shaft of the power-adjustable drive machine (1) The hub (21) is held in a rotationally fixed manner and axially via an inner circlip against a drive side of a pinion (36) (sun gear) projecting shaft journal (7) is set, the pinion (36) for The output shaft (13) has a thrust bearing and has helical teeth. File 5751 P • r up · ι ■> ι • ti · β · * · ·, r> % «ι, 17. Additional control gear according to claims 11 to 16, characterized in that that the stepless intermediate gear (46) on the drive side is in drive connection with the central wheel (35) and, on the output side, with an extension part of the output shaft (13) that can rotate relative thereto, the output wheel (14) being arranged downstream of the continuously variable transmission (46) is. File 5751 F ps