Hydrodynamic-mechanical power transmission device
Patent Information
- Application Number
- EP2023753863
- Authority / Receiving Office
- EP · EP
- Patent Type
- Applications
- Current Assignee / Owner
- Priority Date
- 2022-08-18
- Filing Date
- 2023-08-03
- Publication Date
- 2025-06-25
AI Technical Summary
Existing hydrodynamic-mechanical power transmission devices for variable-speed work machines are either large and inefficient or require additional components for high power transmission, lacking a simple and compact design that can adapt to various operational requirements.
A hydrodynamic-mechanical power transmission device featuring a basic gear configuration with a hydrodynamic converter and planetary gear, including a ring gear, sun gear, and planet carrier, with an additional gear stage for adapting to specific requirements, allowing for compact and efficient high-power transmission without the need for additional clutches or complex enclosures.
Enables compact and efficient power transmission with high power density, adaptable to various operational conditions, and allows for load-free starting based on converter filling state, reducing component complexity and cost.
Smart Images
Figure 1.1
Abstract
Description
[0001] Hydrodynamic-mechanical power transmission device
[0002] The invention relates to a hydrodynamic-mechanical power transmission device, in particular with the features of the preamble of claim 1. The invention relates in particular to a hydrodynamic-mechanical power transmission device for driving a variable-speed work machine.
[0003] Hydrodynamic-mechanical power transmission devices for driving a variable-speed working machine are already known in various designs from the state of the art.
[0004] A generic power transmission device comprises an input for at least indirect connection to a drive unit with a constant speed and at least one output for connection to a work machine with a variable speed. Furthermore, a hydrodynamic converter and at least one superposition gear designed as a planetary gear, comprising a ring gear, a sun gear, and a planet carrier with multiple planets as elements of the planetary gear, are provided. The power is transmitted via a mechanical and a hydrodynamic power branch. The input is connected to a pump wheel of the hydrodynamic converter and a first element of the superposition gear. A turbine wheel of the hydrodynamic converter is connected to a second element of the superposition gear, and the output is at least indirectly connected to a third element of the superposition gear.
[0005] In a design described in DE 3441 877 A1, the hydrodynamic power branch runs through a hydrodynamic converter in the form of a constant velocity converter, and its speed can be regulated by adjusting the blades of the converter's stator. This is recombined with the mechanically transmitted power branch in the superposition gear and thus drives the driven machine at the desired speed, even though the drive unit, which drives the power transmission unit at the input shaft, runs at a constant speed. Based on this design, DE 10 2008 034 607 describes a similar design, in which the hollow shaft used there is replaced by coupling shafts running parallel to the central axis of the power transmission unit.
[0006] The hydrodynamic converter in such power transmission devices between a prime mover and a driven machine, particularly a driven machine, must meet various requirements. Key criteria include the achievable efficiency, the power consumption characteristics, and the change in torque and speed at the output, i.e., the turbine wheel. In known power transmission devices, the operating conditions are influenced by adjusting the stator and / or the degree of filling of the hydrodynamic converter with working fluid.
[0007] From the publication WO2012143123 A1, a power transmission device is previously known which has a hydrodynamic counter-rotating converter instead of a hydrodynamic constant velocity converter. Although the counter-rotating converter is characterized by a lower efficiency than a constant velocity converter, it allows for a very simple and compact design of the entire power transmission device. The first element of the planetary gear of the superposition gear is formed by the planet carrier, while the second element is formed by the sun gear of the planetary gear, and the third element is formed by the ring gear of the planetary gear.This design, in which the ring gear is connected to the output shaft directly or via another gear, preferably a spur gear, and in which the hydrodynamic power branch is input via the sun gear, has the decisive advantage that the planetary gear can be designed very compactly due to the favorable speeds.
[0008] To transmit high power, existing designs are very large or require additional speed-torque transmission devices. The object of the invention is to develop a power transmission device that can be used to transmit very high power while maintaining a very simple and compact design. Furthermore, the overall system should be designed in such a way that a wide range of requirements regarding transmission ratios and the relative arrangement of input and output can be easily implemented.
[0009] The object is achieved according to the invention by an embodiment according to the independent claims. Further advantageous embodiments of the present invention can be found in the subclaims.
[0010] A hydrodynamic-mechanical power transmission device, comprising an input shaft for at least indirect connection to a drive unit with a constant speed and at least one output shaft for connection to a work machine with a variable speed; a basic transmission configuration with a hydrodynamic converter and a superposition transmission designed as a planetary gear, comprising a ring gear, a sun gear and a
[0011] Planetary carrier with a plurality of planets as elements of the planetary gear, wherein the input shaft is connected to a pump wheel of the hydrodynamic converter and a first element of the superposition gear, a turbine wheel of the hydrodynamic converter is connected to a second element of the superposition gear, and the output shaft is connected at least indirectly to a third element of the superposition gear;is characterized in that the first element of the superposition gear is formed by the ring gear, the second element of the superposition gear is formed by the sun gear, and the third element of the superposition gear is formed by the planet carrier. In the power transmission direction, a further gear stage is arranged between the superposition gear and the output shaft, comprising an input and an output, wherein the input of the gear stage is connected to the planet carrier of the superposition gear and the output of the gear stage is connected to the output shaft of the power transmission device or forms this. A hydrodynamic converter is understood to be a device for speed / torque conversion. This comprises at least three paddle wheels which form a working chamber that can be filled with an operating medium and which deflect the flow of an operating medium.
[0012] The term “shaft” is to be understood functionally and includes any design of components that are designed to rotate and rotate around an axis of rotation and that are suitable for transmitting torque.
[0013] A basic transmission configuration within the meaning of the invention specifically refers to a basic arrangement of the converter and superposition gearing in the form of a planetary gear. This can be provided as a modular unit consisting of both prefabricated components or can be assembled from individual converter and superposition gearing modules in the form of a planetary gearing.
[0014] The solution according to the invention offers the advantage of creating a basic transmission configuration consisting of a hydrodynamic converter and planetary gear. This, with the described connection, allows power transmission in two power branches, enables output via the carrier, and is designed for high power ranges. Adaptation to the specific application requirements with regard to the transmission ratio and output alignment is achieved by an additional downstream transmission stage. The basic transmission configuration can be provided as a prefabricated modular unit, which can be easily completed by adding the additional transmission stage, which is preferably also designed as a modular unit, to adapt to a wide variety of requirements.
[0015] The combination of converter and superposition gear with the connection described can also dispense with an additional hydrodynamic coupling for starting, since the function of load-free starting can be achieved via the converter alone, depending on the fill level of the converter. In a particularly advantageous embodiment, the turbine wheel of the converter is connected to the sun gear of the superposition gear on the side of the superposition gear facing the converter, wherein the maximum radial extent of the components that create the connection between the turbine wheel and sun gear is smaller in the radial direction than the diameter of the superposition gear. In other words, the connection between the turbine wheel and sun gear is direct, i.e. without routing them around the superposition gear and thus along the shortest route viewed in the axial direction between the input and output of the power transmission device.The high-speed rotating components are characterized by a significantly smaller diameter compared to the outer diameter of the superposition gear itself, allowing the basic transmission configuration of the converter and superposition gear to be very compact overall, eliminating the need for complex housing of the epicyclic gear by routing the connecting shaft between the turbine wheel and sun gear. The connection between the turbine wheel and sun gear, as a high-speed rotating component with a small diameter, is advantageous in terms of power density and simplifies the mounting of the individual shafts of the superposition gear.
[0016] There are a number of options for implementing the connection between the turbine wheel and the sun gear. However, these primarily involve rotationally symmetrical components, particularly in the form of hollow shafts.
[0017] In an advantageous further development, the rolling bearings usually used in planetary gear drives to support the planetary gears are replaced by plain bearings in this design for low-wear operation.
[0018] For this purpose, according to a first embodiment, the planetary carrier of the superposition gear can be designed with fixed planetary gear pins, with the planetary gears then being slide-mounted on the planetary gear pins. In a second alternative embodiment, the planetary gears are formed integrally with the planetary gear pins or are connected to them in a rotationally fixed manner, and the planetary gear pins are slide-mounted in the planetary carrier. Depending on the requirements of the application, according to a first embodiment, the input and output of the hydrodynamic-mechanical power transmission device can be arranged coaxially to one another, and according to a second embodiment, eccentrically to one another. This is achieved in particular by the design of the additional gear stage.
[0019] The additional gear stage can be designed in a variety of ways depending on the desired gear ratio. However, a configuration that is compact, with as few components as possible, and also small in size is preferred.
[0020] According to a first advantageous embodiment with a coaxial design of input and output, or drive and output, the gear stage is designed as a planetary gear device, comprising at least one lockable or housing-fixed planet carrier, planetary gears, and a gear meshing with the planetary gears, which is at least indirectly, preferably directly, coupled to the planet carrier of the superposition gear, and a sun gear meshing with the planetary gears of the gear stage, which is coupled to the output of the power transmission device or is formed integrally with it. This design is characterized by its small installation space requirement in both the axial and radial directions.
[0021] In a first variant of this first embodiment, the planetary gear device of the gear stage is designed as a simple planetary gear stage, wherein the gear meshing with the planetary gears of the gear stage is formed by a ring gear of the planetary gear stage. This allows sufficient transmission ratios between the superposition gear and the output, thus providing small torques at the output while maintaining a compact design in both radial and axial directions. The use of simple planetary gear sets in the downstream gear stage also allows the use of standardized, prefabricated planetary gear sets. This solution offers not only space advantages but also considerable cost advantages. In a second variant, the hydrodynamic-mechanical power transmission device is characterized in that the planetary gear device of the gear stage is designed as a stepped planetary gear set.This comprises first and second planetary gears designed as stepped planetary gears with different tooth diameters, wherein the gear of the planetary gear device of the gear stage connected to the output of the superposition gear is designed to mesh with the first stepped planetary gears, and the sun gear of the planetary gear device of the gear stage is designed to mesh with the second stepped planetary gears.
[0022] Depending on the design of the gear of the planetary gear device connected to the output of the superposition gearing as a ring gear or sun gear and the design of the gear connected to the output or forming the output as a sun gear, low speeds and high torques can be achieved by grading and introducing the torque into the gear stage via the ring gear on the output side of the gear stage, while still maintaining a relatively compact structure. A first sub-design, in which the gear of the planetary gear device of the gear stage connected to the output of the superposition gearing and meshing with the first planet gears is formed by a ring gear, allows larger gear ratios than a design according to a second sub-variant, in which the gear of the planetary gear device of the gear stage connected to the output of the superposition gearing and meshing with the first staged planet gears is formed by a sun gear.
[0023] While the design of the gear stage as a planetary gear device allows for very compact units in the radial and axial directions with the possibility of realizing high gear ratios, in a second variant the additional gear stage comprises at least one spur gear stage if an eccentric arrangement is desired between the input and output of the power transmission device. Very high gear ratios can already be achieved by designing the spur gear stage as a single-stage spur gear stage, whose input is connected to the superposition gearing and whose output is coupled to or forms the output of the power transmission device. Where the available installation space is limited, these ratios can be further increased in the radial direction by designing it as a multi-stage spur gear stage, whose input is connected to the superposition gearing and whose output is coupled to or forms the output of the power transmission device.
[0024] As already mentioned, the individual components can be provided as modules and assembled in a modular fashion. This applies in particular to the torque converter and superposition gear unit of the basic transmission configuration, as well as to the additional transmission stage. The basic transmission configuration can be assembled from the modular units of torque converter and superposition gear unit, or the entire basic configuration can be offered as a pre-assembled unit. The design and assembly from prefabricated and, where possible, standardized modular units offers the advantage of reducing the number of parts while simultaneously allowing for a wide range of power transmission variants.
[0025] The hydrodynamic converter can be designed in various ways, but is preferably designed as a variable speed converter comprising at least one pump wheel, one turbine wheel, and at least one stator wheel, wherein one of the wheels preferably has adjustable blades or blade segments. According to a particularly advantageous embodiment, variable speed vanes are provided on the stator wheel, thereby achieving improved efficiency and a spread of the characteristic map. The solution according to the invention with adjustment of at least individual variable speed vanes and / or adjustable blade segments offers the advantage of controllable power input and an increase in the possible operating range of the converter within the power transmission device.
[0026] The converter of the power transmission device according to the invention is designed as a synchronous converter. In this case, the impeller and turbine wheel rotate in the same direction, enabling easy connection of the superposition gear in the manner described. The invention is explained below with reference to figures. The figures show in detail:
[0027] Fig.1 shows in a simplified schematic representation the basic structure of a power transmission device;
[0028] Fig. 2 shows an embodiment of the power transmission device according to Figure 1 with a downstream gear stage in the form of a simple planetary gear set;
[0029] Fig. 3 shows an embodiment of the power transmission device according to Figure 1 with a downstream gear stage with a single-stage planetary gear;
[0030] Fig. 4 shows an embodiment of the power transmission device according to Figure 3 with a downstream gear stage with an alternative embodiment of a single-stage stepped planetary gear;
[0031] Fig. 5 shows an embodiment of the power transmission device according to Figure 1 with a downstream gear stage with a simple spur gear stage;
[0032] Fig. 6 shows an embodiment of the power transmission device according to Figure 1 with a downstream gear stage with a multi-stage spur gear stage;
[0033] Figure 1 illustrates, in a simplified schematic representation, the basic structure of a hydrodynamic-mechanical power transmission device 1 designed according to the invention, hereinafter referred to as a power transmission device for transmitting power from a drive machine 2 to a machine to be driven, in particular a work machine 3. The power transmission device 1 comprises at least one input for introducing torque and at least one output. The power transmission device 1 is particularly designed to be suitable for transmitting power from a drive machine 2 with a constant speed to a work machine 3 operable at a variable speed. For this purpose, the input is designed as an input shaft E for at least indirect connection to the drive machine 2. The output is formed by an output shaft A for at least indirect connection to a work machine 3.An at least indirect connection is understood to mean both a direct connection and a connection via further intermediate components, which may also include devices for speed-to-torque conversion.
[0034] The power transmission device 1 comprises a hydrodynamic speed / torque converter, hereinafter referred to as the hydrodynamic converter 4, and a superposition gear 5, as well as a gear stage 6 arranged between the superposition gear 5 and output A for adaptation to different required transmission ratios and / or installation situations. The hydrodynamic converter 4, the superposition gear 5, and the gear stage 6 are arranged downstream of one another in the axial direction between the input shaft E and the output shaft A.
[0035] For this purpose, the superposition gear 5 has an input 12 and an output 13. The input 12 of the superposition gear 5 is coupled to the converter 4 and the input E of the power transmission device 1. The output 13 of the superposition gear 5 is connected to an input 14 of the gear stage 6. The output 15 of the gear stage 6 is coupled to the output or output shaft A of the power transmission device or forms this.
[0036] According to a first embodiment shown in Figure 1, the input shaft E and output shaft A of the power transmission device 1 can be arranged coaxially to one another or eccentrically.
[0037] The superposition gear 5 is designed as a planetary gear 7, comprising at least one ring gear 8, a sun gear 9, and a planet carrier or carrier 11 supporting the planet gears 10. The planet gears 10 are rotatably mounted on the carrier 11. The mounting can be implemented such that the carrier 12 has fixed planet gear pins 22, and the planet gears 10 are rotatably mounted thereon. An alternative design involves a rotatable mounting of the planet gear pins 22, which support the planet gears 10 in a rotationally fixed manner.
[0038] The hydrodynamic converter 4 comprises at least one pump wheel P, one turbine wheel T and one guide wheel L. The converter 4 is designed as a single-phase hydrodynamic converter or synchronous converter, i.e. the pump wheel P and the turbine wheel T rotate in the same direction.
[0039] Other designs are also conceivable, for example multi-stage converters.
[0040] The converter 4 is designed as a control converter for additional modification of the circulating flow and thus the characteristic curve. For this purpose, the blading of at least one of the elements—the impeller P, the turbine wheel T, or the stator L—comprises one or a plurality of control vanes or adjustable vane segments. In the illustrated case, an adjustment device 28 for adjusting the vanes is particularly advantageously assigned to the stator L.
[0041] The converter 4 and the superposition gear 5 are arranged one behind the other in the axial direction between input E and output A. The additional gear stage 6 is functionally and structurally subordinate to the superposition gear 5, viewed in the axial direction. The converter 4, the superposition gear 5, and the gear stage 6 can be kept as prefabricated and pre-assembled modules and combined with one another according to application requirements. The modular design has the advantage of being able to meet different application conditions quickly and with minimal effort using as few basic components or modules as possible.
[0042] According to the invention, the pump impeller P of the converter 4 is coupled to the input E and at least indirectly in a rotationally fixed manner to the ring gear 8 of the planetary gear 7, while the turbine wheel T is connected to the sun gear 9. The planet carrier or web 11 forms the output 13 of the superposition gear 5. The hydrodynamic converter 4 and the planetary gear 7 are arranged coaxially with one another. The coupling structure designed in this way and connected to the converter 4 allows the transmission of high power at the output of the superposition gear. To adapt the speed when coupling the power transmission device 1 to the driven machine 3 or to achieve the required overall transmission ratio, a gear stage 6 is arranged downstream of the superposition gear 5.The gear stage 6 comprises an input 14, which is connected to the output 13 of the superposition gear 5, and an output 15, which forms the output A of the power transmission device 1 or is connected thereto.
[0043] Input E and output A of the power transmission device 1 are arranged either coaxially or eccentrically, as shown in Figure 1. The specific design depends on the respective application.
[0044] There are a number of options regarding the design of the gear stage 6. If coaxial arrangements of input E and output A are required, gear stages 6 in the form of planetary gear devices are preferably used, which can be designed as a simple planetary gear set or planetary gear stage arrangements. Possible embodiments are shown in Figures 2 to 4, which reproduce designs of the power transmission device 1. What the gear stages 6 shown there have in common is that they comprise a planetary gear device 16 with at least one stationary, in particular fixed web or planet carrier 17 and a sun gear 18, which forms the output 15 of the gear stage 6 or is connected to it. For this purpose, the planet carrier 17 is either mounted in a stationary manner, in particular fixed to the frame, or alternatively is actively held via a braking device (not shown).The input 14 of the gear stage 6 is formed by another element of the planetary gear device 16.
[0045] Figure 2 shows a design of the downstream gear stage 6 as a simple planetary gear set 19, whose input 14 is formed by the ring gear 20. The connection between the ring gear 20 of gear stage 6 and the planet carrier 11 of the superposition gear 5 is guided outside the outer diameter of the superposition gear 5. The sun gear 18 is arranged coaxially with the input E of the power transmission device 1 and forms the output A of the power transmission device 1 or is connected to it in a rotationally fixed manner. The planet gears 21 of the planetary gear set 19 of the planetary gear device 16 mesh with the ring gear 20 and the sun gear 18. The sun gear 18 and the ring gear 20 are arranged in an axial plane.
[0046] Figures 3 and 4 show embodiments of planetary gear devices 16 with stepped planets, in particular a stepped planet with a step through the use of so-called stepped planet gears 21.1 and 21.2. The stepped planet gears 21.1, 21.2 are preferably mounted coaxially to one another on the planet carrier 17 and can be present on an integrally formed component with different tooth diameters or as individual, separate stepped planet gears 21.1, 21.2 that are connected to one another. In this case, they are preferably rotatably mounted on a planet gear bolt 22 that is rigidly connected to the planet carrier 17 or formed integrally on the planet carrier 17. It is also conceivable to design the stepped planet gears 21.1, 21.2 as separate or interconnected gears that are mounted on a rotatably mounted planet gear bolt 22.
[0047] Hydrodynamic converter 4 and superposition gear 5 correspond to the design shown in Figure 2.
[0048] In Figure 3, the planetary gear device 16 of gear stage 6 is designed with a single-stage stepped planetary gear. The input 14 of gear stage 6 is formed by a ring gear 20, which meshes with first stepped planetary gears 21.1. The first stepped planetary gears 21.1 are coupled to the second stepped planetary gears 21.2, in particular via the shared and positioned planet carrier 17. The output 15 is formed by a sun gear 18, which meshes with the second stepped planetary gears 21.2. The first stepped planetary gears 21.1 have a smaller tooth diameter than the second stepped planetary gears 21.2. This results in a lower gear ratio. The desired gear ratio can be adjusted by selecting the tooth diameters of the stepped planetary gears 21.1, 21.2.
[0049] Figure 4 shows an alternative embodiment of a gear stage 6 compared to the embodiments in Figures 2 and 3. The planetary gear device 16 also comprises a stepped planet with first and second stepped planetary gears 21.1, 21.2 with a common bearing axis. Compared to the embodiment in Figure 3, the input 14 of the gear stage 16 is formed by a sun gear 23, and the output by a sun gear 18 meshing with the second stepped planetary gears 21.2. By locking the planet carrier
[0050] Figures 5 and 6, on the other hand, show embodiments of the power transmission device 1 with gear stages 6 in the form of spur gear stages, which are mainly used for applications with a required offset between input E and output A.
[0051] Figure 5 shows a simple spur gear stage 25 comprising an even number, in particular two, spur gears 26 and 27 that mesh with each other. Spur gear 26 forms the input 14 of gear stage 6 or is connected to it, and spur gear 27 forms the output 15 of gear stage 6 or is connected to it. This type of gear stage 6 is very compact in the axial direction. However, to achieve a high transmission ratio with this design, spur gear 26 must be designed with a correspondingly large diameter.
[0052] In order to keep the installation space as compact as possible in the radial direction, a design of the gear stage 6 as a spur gear transmission 29 with two spur gear stages 30 and 31 connected in series is proposed according to Figure 6, wherein the output 32 of the first spur gear stage 30 is connected to the input 33 of the second spur gear stage 31 and these are arranged coaxially to one another. The first spur gear stage 30 comprises a first spur gear 36, which forms the input 34 of the first spur gear stage and thus also the input 14 of the gear stage 6. This meshes with a spur gear 37, which forms the output 32 of the first spur gear stage 30. The output 37 is coupled to the input 33 of the second spur gear stage 31, which is formed by a first spur gear 38. Both spur gears 37 and 38 are mounted on a common shaft. The output 15 of gear stage 6 is formed by the gear 39 of the second spur gear stage 31 and is mounted on the output shaft A.There are a multitude of options with regard to the adjusting devices 28 to be designed for the blading of the converter 4 for the embodiment according to Figures 1 to 6. These can be designed in a wide variety of ways and differ in terms of the implementation of a plurality of sub-functions, which include the type of generation of the adjusting force, the direction of introduction of the adjusting force, the type of adjustment of the individual adjusting blade or the adjustable blade segment and the type of blade control. With regard to the type of control, a distinction can be made between central control, i.e. adjustment of all adjusting blades and / or adjustable blade segments or individual or group control of the adjusting blades and / or adjustable blade segments. The specific selection is made according to the requirements of the application.
[0053] List of reference symbols
[0054] 1 power transmission device
[0055] 2 drive machine
[0056] 3 working machines
[0057] 4 converters
[0058] 5 superposition gears
[0059] 6 gear stages
[0060] 7 planetary gears
[0061] 8 ring gear
[0062] 9 Sun gear
[0063] 10 planetary gears
[0064] 11 Web, planet carrier
[0065] 12 Input superposition gear
[0066] 13 Output superposition gear
[0067] 14 Input gear stage
[0068] 15 Output gear stage
[0069] 16 Planetary gear device
[0070] 17 Planet carrier; web
[0071] 18 Sun gear
[0072] 19 Planetary gear set
[0073] 20 ring gear
[0074] 21 planetary gears
[0075] 21.1 , 21.2 Stepped planetary gear
[0076] 22 planetary gear bolts
[0077] 23 Sun gear
[0078] 25 spur gear stage
[0079] 26 first spur gear
[0080] 27 second spur gear
[0081] 28 Adjusting device
[0082] 29 Spur gear 30 Spur gear stage
[0083] 31 Spur gear stage
[0084] 32 Output first spur gear stage
[0085] 33 Input second spur gear stage 34 Input first spur gear stage
[0086] 35 Output second spur gear stage
[0087] 36 first spur gear
[0088] 37 second spur gear
[0089] 38 first spur gear 39 second spur gear
[0090] E Input; input shaft of the power transmission device
[0091] A Output; output shaft of the power transmission device
[0092] P Impeller
[0093] T Turbine wheel L Stator
Claims
Patent claims 1. Hydrodynamic-mechanical power transmission device (1), comprising an input shaft for at least indirect connection to a drive unit, in particular a drive machine (2) with constant speed and at least one output shaft for connection to a working machine (3) with variable speed; a basic transmission configuration with a hydrodynamic converter (4) and a superposition gear (5) designed as a planetary gear (7), comprising a ring gear (8), a sun gear (9) and a planet carrier (11) with a plurality of planet gears (10) as elements of the planetary gear (7), wherein the input shaft (E) is connected to a pump wheel (P) of the hydrodynamic converter (4) and a first element of the superposition gear (5), a turbine wheel (T) of the hydrodynamic converter (4) is connected to a second element of the superposition gear (5), and the output shaft (A) is connected at least indirectly to a third element of the superposition gear (5);characterized in that the first element of the superposition gear (5) is formed by the ring gear (8), the second element of the superposition gear (5) is formed by the sun gear (9) and the third element of the superposition gear (5) is formed by the planet carrier (11), and in the power transmission direction between the superposition gear (5) and the output shaft (A) an additional gear stage (6) is arranged, comprising an input (14) and an output (15), wherein the input (14) of the gear stage (6) is connected to the planet carrier (11) of the superposition gear (5) and the output (15) of the gear stage (6) is connected to the output shaft (A) of the power transmission device (1) or forms the output shaft thereof; 2. Hydrodynamic-mechanical power transmission device (1) according to claim 1, characterized in that the turbine wheel (T) is arranged on the side facing the converter (4) facing side of the superposition gear (5) is connected to the sun gear (9) of the superposition gear (5), wherein the maximum radial extension of the connection between the turbine wheel (T) and the sun gear (9) realized components, viewed in the radial direction, is smaller than the diameter of the superposition gear (5). Hydrodynamic-mechanical power transmission device (1) according to claim 1 or 2, characterized in that the planet carrier of the superposition gear is designed with fixed planet gear bolts and the planet gears are slide-mounted on the planet gear bolts or the planet gears are formed integrally with the planet gear bolts or are connected thereto in a rotationally fixed manner and the planet gear bolts are slide-mounted in the planet carrier. Hydrodynamic-mechanical power transmission device (1) according to one of claims 1 to 3, characterized in that the input shaft (E) and output shaft (A) of the hydrodynamic-mechanical power transmission device (1) are arranged coaxially to one another.Hydrodynamic-mechanical power transmission device (1) according to one of claims 1 to 3, characterized in that the input shaft (E) and output shaft (A) of the hydrodynamic-mechanical power transmission device (1) are arranged eccentrically to one another.Hydrodynamic-mechanical power transmission device (1) according to one of claims 1 to 5, characterized in that the gear stage (6) is designed as a planetary gear device (16), comprising at least one lockable or housing-fixed planet carrier (17), planet gears (21) and a gear meshing with the planet gears (21), which is at least indirectly, preferably directly, coupled to the output (13) of the superposition gear (5), in particular the planet carrier (17) of the superposition gear (5), and a sun gear (18) meshing with the planet gears (21) of the gear stage (6), which is coupled to the output shaft (A) of the power transmission device (1) or is formed integrally therewith. Hydrodynamic-mechanical power transmission device (1) according to claim 6, characterized in that the planetary gear device (16). is designed as a simple planetary gear stage, wherein the gear meshing with the planetary gears (21) of the gear stage (6) and coupled to the superposition gearing (5) is formed by a ring gear (20) of the planetary gear stage. Hydrodynamic-mechanical power transmission device (1) according to claim 6, characterized in that the planetary gear device (16) of the gear stage (6) is designed as a stepped planetary gear set, comprising first and second planetary gears designed as stepped planetary gears (21.1, 21.2) with different tooth diameters, wherein the gear of the planetary gear device (16) of the gear stage (6) connected to the output (13) of the superposition gearing (5) meshes with the first stepped planetary gears (21.1), and the sun gear (18) of the planetary gear device (16) of the gear stage (6) meshes with the second stepped planetary gears (21.2).Hydrodynamic-mechanical power transmission device (1) according to claim 8, characterized in that the gear of the planetary gear device (16) of the gear stage (6), which gear is connected to the output (13) of the superposition gear (5) and meshes with the first planetary gears, is formed by a ring gear (20). Hydrodynamic-mechanical power transmission device (6) according to claim 8, characterized in that the gear of the planetary gear device (16) of the gear stage (6), which gear is connected to the output (13) of the superposition gear (5) and meshes with the first planetary gears, is formed by a sun gear (23). Hydrodynamic-mechanical power transmission device (1) according to one of claims 1 to 5, characterized in that the additional gear stage (6) is designed as a single-stage spur gear stage (25), the input (14) of which is connected to the superposition gear (5) and the output (15). Output (15) is coupled to the output shaft (A) of the power transmission device (1) or forms the same. Hydrodynamic-mechanical power transmission device (1) according to one of claims 1 to 5, characterized in that the additional gear stage (6) is designed as a multi-stage spur gear stage, the input (14) of which is connected to the superposition gear (5) and the output (15) of which is coupled to the output shaft (A) of the power transmission device (1) or forms the same. Hydrodynamic-mechanical power transmission device (1) according to one of claims 1 to 12, characterized in that the additional gear stage (6) and the basic transmission configuration or its individual components, converter (4) and superposition gear (5), are designed as modular units.Hydrodynamic-mechanical power transmission device (1) according to one of claims 1 to 13, characterized in that the hydrodynamic converter (4) is designed as a synchronous converter. Hydrodynamic-mechanical power transmission device (1) according to one of claims 1 to 14, characterized in that the hydrodynamic converter (4) is designed as a control converter and comprises a pump wheel (P), a turbine wheel (T), and at least one guide wheel (L), wherein preferably at least one of the wheels comprises adjustable blades or blade segments.