DE3714859A1 - Combination gearing for small wind and water power plants - Google Patents

Abstract

An infinitely-variable-speed gearing component with automatic speed control in the transmission path between the prime mover and the driven machine creates the preconditions for generating constant-frequency electricity for covering the base demand of an independent supply system (isolated operation). This provides the freedom and precondition for adjusting the speed of the prime mover to optimise output, so that efficient acquisition and conversion of this clean, renewable energy can occur. The integration of all components, including the prime mover and driven machine, or at least their bearing blocks, into or on a common gearbox results in a compact, weight-saving design with low capital costs. Further examples of characteristics of the invention are an automatic control device for the prime mover speed and loading, integrated into the gear train, which responds to deviations from a specified speed ratio between the speed of the prime mover and the speed of a reference rotor running substantially proportionally to the speed of the wind or water current; or the locating of a hydraulic pump as driven machine in a rigid transmission path, so that the supply of energy exceeding the base demand can be converted into heat and transferred to a heat exchanger or heat store.

Description

Gear combination for transferring and converting Speed and torque between the engine and the machine in small wind and water power plants with devices for regulating the generator speed as well as for performance-optimizing adjustment of the engine speed to the flow velocity of the Drive medium wind or water.

When using regenerative, "clean" energy such as Wind and hydropower and their implementation in electrical Energy is particularly the efficiency of capturing and Conversion, but also the minimization of plant costs of special interest. Are also operational security and longevity of the system and its components an important selection criterion and decisive for the profitability of such concepts.

Known, common, especially in "wind farms" Drive concepts used exist at Example from a wind turbine, multi-step transmission and an electric generator, that feeds into an existing network and this is also stabilized in terms of speed. The effective conversion of wind energy into kinetic Energy is not taken into account in any way, because the ratio of the rotor blade speeds to the flow velocity, which is only in optimal energy conversion in a certain area  enables, not taken into account or the respective Wind conditions is adjusted.

For the self-sufficient supply of regional supply networks are largely constant generator speeds required. There is a possibility of speed control in addition in "adjusting" the blade position. However, such control systems are very sluggish and imprecise. In addition - especially in the lower speed range - the different flow conditions out; the rotation of the rotor thereby imposing an irregularity.

Load controls have also proven their worth in practice. In order to If the connection between the engine and the machine is rigid, e.g. B. in wind turbine drive by the load whole machine combination to the desired generator speed or to a target engine rotor speed are forced. Such (simple) speed controls but meet the requirements of an efficient Implementation of wind energy in mechanical Energy also not counted.

Such low-pressure engine power plants are general effective if on the one hand a variable Transmission component between the engine and the machine arranged to keep the generator speed constant is, and on the other hand the possibility of one performance - maximizing speed control Engine exists. The drive technology offers already suitable for keeping the generator speed constant speed-controlled gearbox. For example mechanical "Generator drives", which are already used in small hydropower Have proven pilot projects. The is too Use of hydrostatic control gears in wind power test projects known. The latter are still relative  complex additional regulating and control devices required. When using such separate gearbox designs, the other connection and transmission elements require is the construction and investment costs relatively large. When using an engine Speed control come their facilities in addition, which is particularly the case with a separate arrangement the total cost of such objects increases significantly.

A particular disadvantage to be noted with wind turbines the very strong influence is very different occurring wind speeds on the Efficiency and service life or lifespan such systems or their aggregates and components.

Low power losses through the use of smaller ones Components for the efficient acquisition of a "basic service" at low wind speeds on the one hand and consequent risk of overloading and Short-lived, on the other hand, are two contradictions Consequences. Generally, the supply is more self-sufficient Providing consumers and circles with a certain amount of "clean" electrical energy, d. H. at a constant frequency, e.g. B. for electrical appliances Housekeeping, even at a relatively low level Wind speed, a basic requirement. Also should the sporadically occurring energy peaks also in inferior form can be used, e.g. B. for heating purposes or for electrolytic hydrogen production.

Object and purpose of the present inventive concept is the creation of drive and transmission concepts the above for small wind and water power plants reduce technical disadvantages or  avoid and the conventionally relatively high Reduce investment costs. Special goal is a compact and lightweight construction that Wind power plants located on towers are particularly relevant is, as well as an efficient recording and implementation of regenerative forms of energy.

The solution consists in those mentioned in the claims Design and execution features.

The main benefits and advantages are there in this:

•  - the summary and integration of the most essential Components including the engine and work machines in or on a gearbox housing economical and compact solution, continue is the assembly effort, and thus the Substructure (especially the tower in wind power plants) reduced and cheaper,
•  - Stepless transmission components allow because the frequency fidelity of the generated electricity the supply self-sufficient networks (island operation) and through the Adaptation of the engine speed the respective flow velocities of the energy-carrying medium efficient acquisition and implementation of such energies,
•  - separate, robust performance paths for the sporadic resulting energy peaks allow a weaker Interpretation of the regulated power path, whereby this Plant part cheaper and due to the limited load nevertheless the lifespan is increased.
•  - the combination of different elements and components to a unit, e.g. B. several planetary stages to a multiple planetary gear also causes a reduction in construction costs.

Specific advantages of the different embodiments are noted under their descriptions.

Embodiment Fig. 1

Longitudinal section of a gear combination according to the invention with a planetary gearbox and one stepless conical pulley belt transmission in Transmission path, one integrated in the gearbox Wind turbine bearing base with a reference or second small servo and control tasks Wind rotor and one on the common gear housing arranged generator seat and gear swivel base.

Fig. 2

Idealized representation of the force paths of an inventive Wind turbine gear arrangement, consisting out:

•  a) a planetary transmission gear to increase the input speed of the continuously variable transmission
•  b) a planetary superposition gear for driving a flywheel equalizing the rotary motion, especially at low wind turbine speeds the flywheel speed is increased;
•  c) a further superposition gear for the adjustment drive for self-adjusting the Turbine blades.

Fig. 3 to 5

Velocity ray diagrams of Fig. 2, wherein
Fig. 3 of the functional description of component a
Fig. 4 of the functional description of component b
Fig. The functional description of component c 5 serves.

Fig. 6

Schematic representation of a wind turbine with a superposition gear and two electr. Generators and one Wind turbine reference rotor, as well as an integrated Turbine blade adjustment device.

Fig. 7

Schematic representation of a small hydropower plant with one medium bad water wheel.

Fig. 8

Schematic representation of a small hydropower plant with different alternative sensor and control devices.

Fig. 9

Schematic representation of a hydraulic power transmission combination with an Ossberger water turbine and two working machines, the latter consisting of an electric generator to a speed-controlled transmission path and one Hydraulic pump into a rigid transmission path and one Load control that optimizes engine speed.

Fig. 10

Modified schematic representation of FIG. 9 with an inflow regulation.

Fig. 11

Schematic representation of a multi-step transmission for small wind or Hydroelectric power plants with two Working machines: a generator and a hydraulic pump with load control device for speed control of the entire Investment.

Fig. 12

Schematic representation of a transmission with a continuously variable transmission component and one, on appropriate translation adaptation based power control for preferred external Work machine such. B. pumps.  

Description of the exemplary embodiments Fig. 1

Gear housing 1 forms the basic basis of the wind turbine. On or in it are the wind turbine bearing bases 2 , the generator flange base 3 and the rotary base 4 of the housing itself for tracking the wind direction, and the bearing base 5 of the side wind vane required for this. A planetary gear is connected to the wind turbine shaft 6 in the interior of the housing to increase the speed, with the outer sun gear 7 , the non-rotatable planet web 8 with the planet gears 9 , which are in engagement with the inner sun gear 10 . The latter is connected via the gear 11, which is non-rotatable thereon, to the gear 16 seated on the shaft 12 , the conical disk 14 , and leads via the conical disk 15 and gear 19 to the generator 20 .

In the shaft hub 21 are the rotatably mounted rotor blades 22 a, b , with the adjusting linkage 23 , which is actuated by an axially adjustable sleeve 24 . This undergoes its axial movement via the threaded blocks 25 , which in turn are arranged on the further hollow shaft 27 , which is designed as a threaded spindle 26 and is seated in the turbine shaft 6 . This hollow shaft 27 is connected to the web of a further planetary gear 28 described in more detail in FIGS. 2 and 5, which initiates an adjusting rotary movement when there is a deviation in a predetermined speed ratio between the blade peripheral speed and the flow speed of the driving medium. For this purpose, the shaft 29 is located in the hollow turbine shaft 6 with a reference wind rotor 30 in the center of the engine or in front of it for detecting the wind speed. The blade pitch angle can thus be selected and tracked solely on the basis of performance-optimizing criteria. The generator speed is kept constant by the speed-controlled continuously variable transmission 14, 15 .

The main specific advantages of this invention Execution concept are:

•  - By constant generator speed control, the engine speed can be adjusted to optimize performance.
•  - The reference engine provides except for the control processes required actual value messages also servo and in some Dimensions still safe emergency tasks.

To Fig. 2

Multiple planetary gears:

• a) To increase the speed of one or more drive paths. The drive takes place via the engine shaft 6 , planetary web 45 , planetary gear 46 , an inner sun gear 47 , a gear 48 which is fixed against rotation to the driving gear 12 , which in turn forms the transmission base to a working machine.
• b) To increase the speed of a flywheel 49 to stabilize the rotary movement in the low speed range of the engine. The outer sun gear 50 , which is rotatable with the engine shaft 6, guides the power flow via the planet gear 51 , which is seated on a planetary web 52 , via a further inner sun gear 73 and web pins 53 to the inner sun gear 55 of the flywheel 49 . The support base of the planet gear 51 forms the inner sun gear 73 on shaft 74 , which in turn is connected to the constantly running shaft of a control gear.
• c) For automatic adjustment and control of the turbine blade adjustment mechanisms (e.g. for item 28 in Fig. 1). The outer sun gear 56 connected to the engine shaft 6 meshes with the planet gear 91 . This is mounted on planetary web 57 , which is arranged on the hollow shaft 27 , the adjustment drive. Furthermore, planet gear 91 is in engagement with the inner sun gear 58 , which in turn is connected to a reference rotor shaft 29 .

To Fig. 3

Items 60, 61 are extreme drive angular velocity vectors of the drive shaft 6 and the web 45, respectively
62, 63 the assigned angular velocity vectors of the planet gear 46 around the fixed point 64 ,
which gives the inner sun gear 47 and the gear 48 connected to it via pitch point 65 the angular velocity, whereby from pitch point 68 gear 12 about its axis of rotation the angular velocity 69/70 is forced.

To Fig. 4

Pos. 71, 72 are extreme drive speed vectors on the outer sun gear 50,
75 the angular velocity vector of a sun gear 73 connected to the constantly running output path of a control gear.

The peripheral speed of the pitch point 76 gives the planetary web 52 the angular speeds 77, 78 , whereby the planet gear 54 experiences the angular speed 80/81 around the fixed point 79 .

Via the point of engagement 82 , the inner sun gear 55 and thus the non-rotatable flywheel 49 is forced to the angular velocity 83/84 .

The advantage of this planetary arrangement according to the invention is that it causes a high flywheel speed 83 at a low drive speed 71 and a moderate or an insignificantly increased flywheel speed at a high drive speed 72 . As a result, the work and engine rotation is stabilized at low, uneven or non-uniform drive speeds, without this section running too fast at high drive speeds. This also has an advantageous effect on the design conditions; there are no special requirements with regard to speed and moment load.

To Fig. 5

Pos. 85 is the angular velocity vector of the outer sun gear 56 fixed to the engine shaft ,
Item 86 is the angular velocity vector of the inner sun gear 58 fixed to the reference wheel.

The planetary ratio is advantageously designed in such a way that, for a predetermined rotational speed ratio to be maintained, between the bases 56 and 58, which are identical to the engine and machine, z. B. ω ₅₆ / ω ₅₈ 0.5-0.6, the angular velocity of the web 57 and thus also the hollow shaft 27 is zero. Changes z. B. the turbine speed 85 by the amount + Δω ₅₆ = Pos. 87 , the web 57 and thus the rotor blade adjustment drive 27 experience a change in angular velocity to + Δω ₅₇ = Pos. 88 . If 85 decreases by 89 , planetary land 57 undergoes an adjustment movement by - Δω ₅₇ = Pos. 90 .

The present adjustment drive design according to the invention provides a safe, simple and robust conception that without additional or external servo actuation and control devices works.

By combining all three planetary systems into one unit a constructively favorable solution can be achieved.  

Embodiment Fig. 7

The water wheel 160 with its chambers or cells 161 , designed as a medium-sized cellular wheel, utilizes both the weight effect and the impulse force (speed energy) of the water arriving through the channel 162 . The inflow amount is determined by the contactor 163 seated in the dam 164 , which forms a reservoir 165 with its maximum level 166 . In the empty state with the lowest level 167 , this serves only as the flow of water. The waterwheel 160 drives, via the drive shaft 168, a step-by-step transmission 169 , which converts rapidly, a stepless, self-regulating speed converter 170 arranged thereon with the generator 171 . A flywheel 172 is located on the high-speed base of the gear 169 to dampen any irregularities caused by the cell division of the wheel. The inflow speed or the entry speed in the waterwheel determines the accumulation height according to level 166 in the maximum case and the flow rate of the channel flowing through the reservoir in the minimum case. In the present example, the speed range is assumed to be 3: 1. The inflow control by contactor 163 can be accomplished via the adjusting nut 174 acting on the spindle 173 or manually by means of the handwheel 175 or by means of a motor using a hydraulic adjusting motor 176 which converts the adjusting nut. The energy for the servo drive is provided by an oil pump 177 arranged on the variable converter side of the transmission 170 , the pressure line 178 of which leads through a throttle device 179 through line 180 and a return line 181 to the regulating and control device 182 . From there, the pressure medium reaches the switchover element 185 via the lines 183 or 184 , which, when the contactor 163 is actuated manually, allows the pressure medium to circulate without effect. The regulating and control device essentially consists of a hydraulic switching element 186 for three operating stages (circulation and two directionally different inflows and outflows to the servomotor) and two counteracting actuators 184 and 188 . Actuator 184 is designed as a pressure cylinder with pistons 189 tapping their adjacent pressure spaces 190, 192 via lines 192 and 193 before and after throttle point 179, pressure line 179 . The force exerted by the piston 189 on the switching element 186 is directly proportional to the pressure difference at the throttle 179 . Actuator 188 is a pressure housing with a membrane 184 , the pressure spaces 185 and 186 of which they act on both sides and lead via lines 197 and 198 to a flow rate measuring probe 199 , which is designed as a Pitot tube. Instead of a pitot tube, it is also possible, for example, to use a measuring orifice through which the inlet flows or a small impeller projecting into the inlet with an oil pump, the flow of which flows through a throttle point similar to device 179 at a relatively low pressure, for speed measurement. In the case of memories whose filling level or level height alone determines the outflow rate, a flow rate-equivalent signal can be supplied to the regulating and control device 182 by means of mechanical or hydrostatic transducers. On the regulating and control device 182 , the active parts of their actuators and the pressures acting on them are matched to one another in such a way that the pressure difference acting on the piston 189

and
Membrane 184

in terms of strength at a given speed ratio to be observed
v _Rad / v _inflow = 0.5
to be in balance. If the balance of forces is disturbed due to the speed, the control member 182 issues a corresponding, correcting control command to the actuator 176 for changing the inflow quantity or changing the wheel line and thus its speed.

To Fig. 8

The waterwheel 20 drives the electric generator 207 via its ring gear 202, the angular drive 203 , the transmission element 204 , the gear transmission 205 , the continuously variable speed converter 206 , which regulates itself at a constant output speed. Via a switching element 208 , e.g. B. in the form of a hydraulically controlled clutch, another work machine, for. B. a pump 209 , can be coupled to the speed-controlled drive path. Item 210 is a consumer system that is primarily to be supplied with electrical current. The speed ratio determining the effectiveness of the energy conversion on the water wheel is obtained on the one hand from the speed sensor 210 in the inflow channel 211 and on the other hand the speed sensor 220 in the transmission 206 . Their speed-proportional output signals in the converters 216, 219 shown act on the signal node or controller 222 , from which an actuating or control signal acts on an actuator 223 . This actuates switching or control elements one after the other to connect further defined power consumers. For example, 223 consists of a hydraulic switching element, which releases the servo circuit, which is supplied by a pump 227 in the transmission 206 , to a hydraulically actuated clutch 208 and which couples or decouples the pump 209, and / or further electrical consumers via electrical switches 225 and 226 228 and 229 switches to the generator network. The matching of the output signals of the associated converters 216-219 with the resulting output signal in 222 , the connection points and the power of the additional loads 228 and 229 , which determines the wheel speed, is advantageously chosen so that the speed ratio v _Radumf. / v _{water is} an optimal ratio for energy conversion of 0.5∼ ± 20%. The following are available as speed sensors 212 or 220 and converters:

for flow rate:
Item 213 Pitot tube Δ p = f (v ²)
Item 214 baffle plate s = f (F) = f (v)
Item 215 Vane wheel speed sensor U = f (v)

for speed:
with pos. 216, 217 oil pump with throttle section pressure difference
Δ p = f (q ²) = f (n ²)
with item 218 centrifugal governor s = f (n)
with item 219 speed sensor U = f (n)

Under the condition that the inflow speed is largely constant and only the amount of water varies with different power reserves of the channel, so that the filling of the wheel chambers cause the performance differences, a constant comparison signal from a setpoint generator 221 can be used as the setpoint value determining the water wheel speed. In this case, the speed sensor 212 in the inflow 211 can be saved.

To Fig. 9

The transmission combination essentially consists of the transmission housing 230 with the engine 231 arranged therein or thereon, the stepped transmission 232 , the continuously variable transmission component 233 with the electric generator 234 and the hydraulic pump 235 arranged therein. The generator 234 is preferably kept at a constant speed via the continuously variable transmission component 233 by means of a regulating and adjusting device, not shown. The engine is held at a power-optimal speed assigned to the flow rate of the driving medium by a load control. For this purpose, in addition to the working turbine runner 236, it also has a runner 237 , which largely serves reference tasks and detects the flow velocity. In addition to this embodiment, there are others, e.g. B. previously arranged impeller-like designs imaginable. The blade formation of these turbine wheels 236 and 237 is coordinated such that an actuating signal is exerted in a control and actuating device 238 when a predetermined speed ratio deviates. This device 238 is predominantly z. B. from a reference rotor fixed threaded spindle 239 , with which in a longitudinal slot 240 of the turbine shaft 241 displaceable threaded link 242 is engaged and the control signals are transmitted to a transmission linkage or system 244 via an attached transmitter flange 243 . In the present embodiment, the power-determining control element 245 consists of a pressure regulator that determines the pressure of the hydraulic pump 235 .

Thus, the drive energy which is not fully used by the electric generator 234 in the form of heat is detected via this power path. This is passed into a heat exchanger 246 from the primary system 247 to a secondary system 248 , which any consumer 249 - preferably household heat consumers - passed on.

With the present small power plant concept, the regenerative energies generated can be efficiently recorded and exploited, the supply of "clean" (frequency-compliant) electricity being ensured and the excess energy in the form of heat being recorded in a useful manner. It is also advantageous that the speed-controlled force path (for an already limited base load) can be made relatively small and thus inexpensive, while the energy peaks are processed by the robust hydraulic pump 235 . This solution concept therefore also increases the operational safety and service life of such systems. Depending on the relationship between the energy supply and the proportion of electrical energy required, it can be advantageous, similar to FIG. 10, to implement a priority or shutdown device for various electrical consumer circuits, which are also controlled by the control device 238 .

To Fig. 10

The present small-scale power plant concept essentially corresponds to FIG. 9. While the above concept is largely geared towards all the energy which arises, for. B. to detect and exploit in running water, this modification serves the metered, consumption-oriented removal of energy preferably from storage facilities. For this purpose, the power supply to the engine 231 is controlled by an inflow quantity regulating device 250, 251, 238 with an optimally optimized speed-inflow speed ratio.

The power control of the working machine 231 is dependent on the consumer, for. B. by a thermostat 252 , which acts on a pressure control valve 253 , which determines the pressure of the pump. To ensure that the energy consumers do not overwhelm the performance of the engine 231 when effectively implemented, a device 254 can be arranged which, before reaching a maximum power point of the engine, secondary consumer groups, z. B. 255 , switches off.

To Fig. 11

The engine 261 , the hydraulic pump 262 and the electric generator 263 are integrated on or in the multi-step transmission 260 . The speed control of all connected power and working machines 261, 262, 263 takes place through a load control of the engine 261 . The total load on the engine 261 is composed of the load on the generator 263 determined by the consumer 267 and the regulated load on the hydraulic pump 262, the power of which is transmitted to the heat exchanger 246 in the form of heat. The power control of the working machine 262 takes place through its variable pressurization by the pressure control member 264 , which in turn is controlled by a speed sensor, e.g. B. is controlled in the form of a centrifugal governor 265 . A priority switching device 266 for various electrical consumer circuits 268, 269 is arranged in parallel in this controlled system, whereby the supply of a primarily electrical supply circuit 267 is ensured with a small range of services.

The advantage and advantage of this small power plant concept lies in the simple execution of a  Speed control and the use of peak loads are less problematic Components for self-sufficient network supply systems (Island operation).

To Fig. 12

Integrated on or in the transmission housing 270 are the engines 271 and the continuously variable transmission component 272 , the output base of which drives an external machine or, alternatively, an associated or integrated machine 276 via a bevel gear 274, 273 and the shaft 275 . The engine 271 has the working rotor 277 and reference rotor 278 , the functional interaction of which is reflected in a control signal 279 is described in FIG. 9. The performance-optimizing engine speed control takes place in that, in the event of a deviation from a predetermined manipulated variable or position 279, the translation of the continuously variable transmission component 272 is changed in such a way by the hydraulic control element 280 that the engine 271 when the consumer imposes a load on the working machines 275 performance is applied so that it is operated in a predetermined, according to its map performance-optimal speed level.

To use the present transmission concept in a wind power plant, the control and actuation of an obligatory holding brake 281 takes place by means of a hydraulic circuit which is provided by means of a hydraulic pump 282 which is driven essentially by the reference rotor 278 and is proportional to wind speed. It is hydr. Control element 283, the braking device 284 both released and closed. The control command for this is provided by the differential pressure of the throttle point 285 , which acts on the control device 287 of the control element 283 . Throttle point 285 and the spring force of the control device 287 are coordinated and the function of the control element is such that the holding brake 281/284 becomes active both under and above a predetermined wind speed and thus delivery rate of the pump 282 . This ensures a simple, safe, self-sufficient mode of operation.

Leave with the present power plant gearbox concept regenerative energies take priority for funding purposes Use (pump drive) efficiently.

Claims (23)

1. Gear combination for wind and water small power plants, consisting essentially of an engine, transmission gear and transmission elements and one or more work machines, characterized in that the gear combination is a continuously variable transmission component ( 14, 15, 107, 206, 223 ), with a Control device for keeping its output base constant and at least one of the following design features:

• a) the transmission housing of the continuously variable transmission components is designed with that of a fixed-stage transmission component ( 1, 169, 206, 232 ) as a structural unit and has a bearing base for an engine rotor ( 6, 241 );
• b) the gear housing ( 1, 206, 170, 233 ) has a flange base ( 3, 171, 207 ) for at least one working machine;
• c) in the case of wind power plants, the gear housing ( 1, 102 ) has a bearing base ( 4 ) for the horizontal swiveling device;
• d) control, adjustment and servo devices ( 25, 28, 182, 216-224, 238, 250, 251, 264, 280 ) are arranged in the transmission housing for adapting the engine speed to the flow rate of the energy-supplying medium wind or water in order to optimize performance.
• e) a further bearing base for a second motor rotor ( 30, 126, 137, 278 ), preferably serving reference or servo tasks, is arranged on the gear housing;
• f) a flywheel ( 49, 172 ) connected to the force path is arranged in the transmission housing.

2. Gear combination for small wind and water power plants, consisting essentially of an engine, transmission gear and transmission elements and one or more work machines, characterized in that at least two work machines are arranged in or on a common gear housing, one of which is an electric generator ( 234, 263 ), a second working machine is a hydraulic pump ( 235, 265 ), furthermore a regulating or control device ( 245, 264 ) for load regulation of the hydraulic pump ( 235, 265 ) is arranged on or in the transmission. 3. Gear combination for wind and water small power plants, consisting essentially of an engine, transmission gear and transmission elements and one or more machines, characterized in that in or on a gear housing ( 270 ) an engine ( 271 ) or its rotor bearing base arranged is furthermore in the power path between the engine and the machine there is a continuously variable transmission component ( 272 ) with a transmission control device ( 238, 280 ) such that if a predetermined speed ratio between the engine speed and the flow rate of the driving medium deviates, the translation of the continuously variable transmission is changed that the engine is forced into a performance-optimal speed range. 4. Gear combination according to claim 1 and 3, characterized in that the continuously variable transmission components made of conical pulley belt drives consist. 5. Gear combination according to claim 1, characterized in that the flywheel arranged in the transmission ( 49 ) via a superposition gear ( 52-55 ) is connected to the power path, which is such that the gear ratio in the connection path to the power path is higher at low engine speed than at high engine speed. 6. Gear combination according to claim 1, characterized in that the step gear ( 28 ) for driving the continuously variable transmission component ( 14, 145 ), the connecting gear ( 52, 53, 54, 55 ) to the flywheel ( 49 ) and a differential gear ( 56, 57, 58 ) for the implementation of speed differences between the engine rotors ( 22, 30 ) in manipulated variables from planetary gears, which as multiple planetary gears - such as. B. in Fig. 2 - are combined into one unit. 7. Gear combination according to claim 1, 2 and 3, characterized in that actuators or control elements in the gear housing ( 1, 25, 27, 56, 58, 230, 238, 260 ) arranged regulating or adjusting device for adjusting the engine speed after a predetermined speed ratio to the wind or water flow speed consists of two mechanisms, each based on a speed-proportional basis of the engine rotor ( 25, 240 ) and a reference rotor ( 29, 227, 239 ), which function in such a way that when a predetermined differential speed is exceeded an adjusting or regulating movement is exerted on the two bases, for example these mechanisms consisting of a threaded link ( 242 ) arranged in the engine rotor shaft ( 241 ) and a threaded spindle ( 239 ) fixed to the reference rotor, or an overlay gear ( 28, 56) -58 ), whose two input paths ( 56, 58 ) are connected to the engine rotor ( 6 ) and reference rotor ( 29 ) and the output path ( 57 ) is connected to an actuator ( 25, 243 ). 8. Gear combination according to claim 1 and 7, characterized in that the actuating device acts on the rotor blade adjusting device of a wind turbine ( 22, 119 ). 9. Gear combination according to claim 1 and 7, characterized in that the actuating device ( 25, 238 ) acts on the guide or moving blade adjusting device of a hydropower machine. 10. Gear combination according to claim 1, 2 and 3, characterized in that the actuating device ( 238 ) is assigned a load control device ( 245, 264, 280 ). 11. Gear combination according to claim 1, 2, 3 and 7, characterized in that the load control device is a hydraulic pressure control member ( 245, 264, 280 ). 12. Gear combination according to claim 1, 2 and 3, characterized in that control or actuators for speed control consist of centrifugal governor ( 269 ). 13. Gearbox combination according to claim 1, characterized in that the control and adjustment device for adjusting and adjusting the flow and engine speed to each other consists of an existing according to claim 7 control and actuating device, which is arranged in an inflow channel of a hydraulic machine throttle device ( 250th ) acts. 14. Gear combination according to claim 1, 2 and 3, characterized in that the preferably designed as a reference rotor, for control or servo tasks serving second engine rotor ( 30, 126, 237 ) arranged within the main engine rotor ( 22, 119, 236 ) or is stored. 15. Gear combination according to claim 1 and 2, characterized in that the control device for load control of the hydraulic pump ( 235, 265 ) consists of a generator speed controlled device which acts on a pressure control valve arranged in the pump drain ( 245, 264 ). 16. Gear combination according to claim 1 and 2, characterized in that the generator speed control device consists of a centrifugal governor ( 269 ). 17. Gear combination according to claim 1 and 2, characterized characterized in that the control device that records the generator speed from a frequency-converting electronic component and the actuator from a proportional There is a solenoid. 18. Gear combination according to claim 1, 2 and 3, characterized in that a control device ( 149, 150, 266 ) for switching on and off different rank consumer circuits, a control device ( 155, 269 ) is assigned, which has the functional feature that it If a predetermined speed ratio between the engine speed and the flow rate of the driving medium shuts off individual consumer circuits ( 144, 145, 267, 268 ). 19. Gear combination according to claim 1, 2, 3 and 7, characterized in that the control device for switching off different ranks Consumer groups from the claim 7 listed design features. 20. Gear combination according to claim 1 and 3, characterized in that the control device for switching off different ranks Consumer circles from one that Ratio of both speeds Electronic component and an electrical Actuator exists. 21. Gear combination according to claim 1, 2 and 3, characterized in that the reference working machine drives a small, largely control and servo-serving hydraulic pump ( 21, 129, 282 ). 22. Gear combination according to claim 1, 2 and 3, characterized in that the arranged on the reference rotor pump ( 21, 129, 282 ) supplies a holding brake ( 13, 132, 84, 281 ) which must be "released" for operation and a control element ( 283 ) is arranged with the following functional features:

• a) the brake ( 13, 132, 281 ) becomes active when the speed falls below a predetermined lower operating speed or wind speed;
• b) the brake is released in the range of a predetermined wind speed range;
• c) after a predetermined wind speed is exceeded, the brake becomes active again.

23. Gear combination according to claim 1, 2 and 15, characterized in that the pressure medium conveyed by the hydraulic pump ( 235, 265 ) - at least part of it - is supplied to a heat exchanger ( 246 ).