DE102018112025A1 - Power transmission device - Google Patents

Abstract

The invention relates to a power transmission device, in detail with the features of the preamble of claim 1. The invention is characterized in that the hydrodynamic speed / torque converter and the hydrodynamic clutch are arranged eccentrically, preferably parallel to each other and via a transfer case arranged in the housing respectively are connectable to the input of the power transmission device to form the two power branches. According to the invention, an axle thrust compensation device is provided.

Description

The invention relates to a power transmission device, in particular with the features of the preamble of claim 1. The power transmission device is particularly suitable for transmitting power from an at least indirectly connected to a drive unit at constant speed input shaft to an at least indirectly connectable to a work machine with variable speed output shaft , The invention further relates to a drive train of a variable-speed work machine, in particular a pump drive, comprising at least one drive unit in the form of a turbine, in particular a steam turbine to a work machine via a power transmission device.

Such power transmission devices are previously known in a variety of prior art designs. In this case, a distinction is made between a first embodiment with controllable hydrodynamic coupling and a second embodiment with mechanical-hydrodynamic power branching. Representative becomes for the second execution on the pamphlets DE 34 41 877 A1 and DE 10 2008 034 607 directed. Both documents disclose a power transmission device for driving a variable-speed work machine, which consists of a hydrodynamic branch and a transmission with a planetary gear. The hydrodynamic power branch is realized via a hydrodynamic converter and can be regulated by the converter in its rotational speed. This is reunited with the mechanically transmitted power branch in a planetary gear and thus drives the machine at the desired speed, although the drive unit, which drives the power unit to the input shaft, runs at a constant speed.

WO 2016/012317 A1 discloses an embodiment of a power split device with power split, in which a realizable via a converter hydraulic power branch and another power branch are arranged eccentrically and are brought together again via a superposition gear. In this further power branch, a hydrodynamic component in the form of a hydrodynamic control clutch can also be provided. The parallel arrangement can take place in the installed position both in a horizontal or vertical plane and in horizontally and vertically staggered planes. The eccentric arrangement offers on the one hand the advantage of being able to dispense with complex rotary joints and on the other hand to provide a power transmission device in a compact design in the axial direction. By the conditional about the parallel arrangement possible integrable translation, the input speed can be varied and translated to the individual hydrodynamic components in a corresponding manner, so that on the one hand can be used on compact small hydrodynamic units, also in a simple manner, the power transmission device in existing Equipment can be retrofitted, without having to provide additional measures, in particular translations. In this case, according to the design of the transfer case, the power transmission device can be adapted in an optimal manner to the requirements of the application. The power transmission takes place in the individual operating areas of the total operating range in each case via different power branches. The hydrodynamic converter is emptied in the case of power transmission via the hydrodynamic coupling. The same applies to power transmission via the converter and a mechanical drive in the other second power branch.

The storage of the hydrodynamic components takes place in a housing and is to be interpreted accordingly to compensate for the axial thrust generated by the flow forces of the individual wheels of the individual hydrodynamic component accordingly. Due to the size of the axial force component, this requires relatively large bearings, which are also subjected to highly dynamic stresses.

The invention was based on the object to minimize the axial thrust.

The solution according to the invention is characterized by the features of claims 1 and 20. Advantageous embodiments are described in the subclaims.

• - mit zumindest einem, mit einem Antriebsaggregat verbindbaren Eingang und einem, mit einer Arbeitsmaschine wenigstens mittelbar verbindbaren Ausgang,
• - mit einem im Kraftfluss zwischen dem Eingang und dem Ausgang angeordneten ersten mechanischen Leistungszweig und einem weiteren zweiten, einen hydrodynamischen Drehzahl-/Drehmomentwandler umfassenden zweiten Leistungszweig, umfassend zumindest ein Pumpenrad, ein Turbinenrad und ein Leitrad, wobei die beiden Leistungszweige mit dem Ausgang über ein Überlagerungsgetriebe verbindbar sind;
• - erster und zweiter Leistungszweig sind parallel zueinander angeordnet und über ein im Gehäuse angeordnetes Verteilergetriebe jeweils mit dem Eingang der Leistungsübertragungsvorrichtung verbindbar bzw. verbunden;
• - erster und zweiter Leistungszweig sind über ein im Gehäuse angeordnetes Summiergetriebe jeweils mit dem Ausgang der Leistungsübertragungsvorrichtung verbindbar bzw. verbunden;
• - die das Turbinenrad des hydrodynamischen Drehzahl-/Drehmomentwandlers tragende Welle ist über zumindest ein Lager im Gehäuse gelagert.

A power transmission device having a housing and the following features:

• with at least one input which can be connected to a drive unit and an output which can be connected at least indirectly with a working machine,
• - With a arranged in the power flow between the input and the output first mechanical power branch and another second, a hydrodynamic speed / torque converter comprehensive second power branch, comprising at least one impeller, a turbine wheel and a stator, the two power branches with the output via a Superposition gear can be connected;
• - First and second power branch are arranged parallel to each other and a in the Housing arranged transfer case in each case connectable to the input of the power transmission device or connected;
• - First and second power branch are connected via a housing arranged in the summing gear in each case with the output of the power transmission device or connected;
• - The turbine wheel of the hydrodynamic speed / torque converter bearing shaft is mounted on at least one bearing in the housing.

According to the invention, an axle thrust relief device is arranged between the turbine wheel of the hydrodynamic speed / torque converter and the bearing to compensate for the axial thrust on the turbine wheel resulting from the operation of the hydrodynamic speed / torque converter. As a result, the axial thrust can be reliably compensated for at very different operating points of the converter without having to design the bearing of the shaft for the maximum thrust conditions.

If the hydrodynamic speed / torque converter considered in the power flow from the input to the output, a device for braking and / or setting of the connectable to the hydrodynamic speed / torque converter input of the superposition gearing, the Achsschubentlastungseinrichtung between the turbine of the hydrodynamic speed / torque converter and the Device arranged for braking and / or setting of the connectable to the hydrodynamic speed / torque converter input of the superposition gearing. In this case, the Achsschubentlastungseinrichtung is preferably designed as a double-acting Achsschubentlastungseinrichtung.

In a particularly advantageous development, the hydrodynamic speed / torque converter has a supply channel for supplying working medium to the working space. The axial thrust relief device has at least one relief element which can be acted upon by at least one pressure chamber which can be filled with pressure medium for applying a counterforce to the thrust force on the shaft, the pressure chamber being coupled to the filling channel of the hydrodynamic rotational speed / torque converter.

According to a particularly advantageous embodiment, the Achsschubentlastungseinrichtung to a thrust balance ring with a feed channel formed therein for a pressure medium, the front side of the thrust balance ring opens into an annular space. There are provided a first side window and a second side window, each axially adjacent and arranged on opposite sides of the thrust balance ring such that a first pressure chamber and a second pressure chamber arise, wherein the first pressure chamber and the second pressure chamber are each downstream on the basis of a labyrinth seal and inflow side via a first throttle point for the first pressure chamber and a second throttle point for the second pressure chamber is in each case a connection to the annular space for the influx of pressure medium. Furthermore, a disc-shaped throttle element engaging in the annular space is provided. The thrust balance ring and the throttle element are arranged so that one of the two components is fixed in the axial direction and the other component follows an axial movement of the associated machine shaft, wherein the first throttle point and the second throttle point reciprocally open and closed by an axial relative movement between the thrust balance ring and the throttle element be so that between the first pressure chamber and the second pressure chamber creates a pressure difference.

With regard to the design of the power transmission device, there are a number of possibilities.

According to a first embodiment, which is particularly compact in the axial direction, the hydrodynamic components are arranged in the axial direction almost free of offset parallel to each other in the two different power branches. The eccentricity essentially determines the size of the power transmission unit in the axial direction.

1. a) Ein zweiter Wandler im zweiten Leistungszweig mit anderer Charakteristik der Wandlung. Der Vorteil besteht in einer Wirkungsgradsteigerung im Drehzahlbereich fallenden Wirkungsgrades des ersten Wandlers.
2. b) Eine zusätzliche Bremse zwischen Turbinenrad der hydrodynamischen Kupplung und Umlaufgetriebe im ersten Leistungszweig.

In an alternative embodiment, the hydrodynamic components are arranged in the axial direction with offset. This is particularly advantageous when additional functional units have to be integrated into the individual power branches. Such additional components may include:

1. a) A second converter in the second power branch with a different characteristic of the conversion. The advantage consists in an increase in efficiency in the speed range falling efficiency of the first converter.
2. b) An additional brake between the turbine wheel of the hydrodynamic clutch and planetary gear in the first power branch.

However, there is also the possibility of integrating the abovementioned additional components in an arrangement of the hydrodynamic components provided in both power branches free of offset in the axial direction.

The power transmission usually takes place via the hydrodynamic coupling and the hydrodynamic converter in different operating ranges. In particular, in order to enable a smooth start-up and to control / regulate the transmission in the first power branch in a partial area of the overall operating range, the hydrodynamic coupling is designed as a control coupling for this purpose. This can be realized in different ways. In the simplest case, this has a control device comprising a scoop tube for influencing the amount of resources. The scoop is adjustable. The adjustability can be done for example with directional component in the radial and / or axial direction.

Other possibilities exist in an active control of Betriebsmittelzufuhr- and / or discharge from the work cycle.

In a further development of the first embodiment, a device for switching through or bridging the hydrodynamic coupling is provided between the input and the output in order to realize a mechanical through drive. The device is formed in the simplest case as a mechanical lock-up clutch. The device for switching through and the hydrodynamic coupling can be switched at least in parallel. The at least parallel shiftability of the hydrodynamic clutch and the shiftable clutch means that each of the clutches can be actuated individually and independently of the other. The power transmission takes place in at least one operating state only via one of the clutches. It is also conceivable that in a further operating state, both clutches can be actuated, wherein the switchable clutch in this state then bridges the still filled hydrodynamic clutch, so that no torque is transmitted via the hydrodynamic clutch itself and still a mechanical drive between input and output is created.

In a particularly advantageous embodiment of the first and second power branch are free of other speed and / or torque converter means, i. only one hydrodynamic coupling and one transducer are provided. In this case, the power transmission device is particularly short.

An inventively designed power transmission device according to a second embodiment with a housing, with at least one, connectable to a drive input and a, at least indirectly connectable with a machine output, with a arranged in the power flow between the input and the output first mechanical power branch and a further second , a hydrodynamic speed / torque converter comprising a second power branch, comprising at least one impeller, a turbine wheel and a stator, wherein the two power branches are connected to the output via a superposition gear, characterized in that the first and second power branch are arranged parallel to each other and over a transfer case arranged in the housing can be connected in each case to the input of the power transmission device and the first mechanical power indicator is free from further rotational speed and / or torque conversion gseinrichtungen is, in particular designed as a mechanical drive-through arrangement and the second power branch is free of addition to the hydrodynamic speed / torque converter provided speed and / or torque converter means.

A mechanical through drive arrangement is understood to mean a direct coupling free of rotational speed and / or torque conversion possibilities between the output of the transfer case and the input of the superposition gear. In the simplest case, this is a connecting shaft arrangement of one or more rotatably connected shafts.

The solution of the eccentric arrangement of hydrodynamic converter and mechanical drive through offers the advantage that on the one hand, in particular in a parallel arrangement can be dispensed with complex rotary joints and on the other hand, a power transmission device can be provided in a compact design in the axial direction. The conditional about the parallel arrangement possible integrable translation, the drive speed in the individual power branches can be varied and translated in a corresponding manner and thus can be better adapted to the specific conditions of use.

The transfer case comprises at least one input, which forms the input of the power transmission device or at least indirectly connected to this rotation. The transfer case comprises at least two outputs which are arranged eccentrically to each other, wherein a first output to the first power branch, in particular the mechanical drive arrangement for the second embodiment or the impeller of the hydrodynamic coupling for the first embodiment is at least indirectly connected and a second output to the Impeller of the hydrodynamic speed / torque converter is connected at least indirectly. As a result, the torque transmission to the individual hydrodynamic components or realized the individual power branches.

With regard to the specific design of the transfer case itself is in terms of the use and training of the hydrodynamic components and the superposition gear a plurality of ways.

The input of the transfer case may be arranged coaxially or eccentrically to an input of the individual power branches, the input being formed by a pump wheel of one of the hydrodynamic components or a shaft of the mechanical drive arrangement. The coaxial arrangement offers the advantage of directly applying one of the power branches to the torque present at the input of the power transmission device, while the eccentric arrangement allows the integration of translations into the power branches slow or fast, thereby optimizing an improved adaptation to the specific application designed components is possible.

According to a first embodiment, the transfer case is designed with a transmission to the slow for the first and / or second power branch while according to a second embodiment, the transfer case can be designed with a translation into fast for the first and / or second power branch. As a result, the basic configuration can be easily adapted to different powertrain requirements without any further changes, merely via the design of the hydrodynamic components and the transfer case.

In an advantageous embodiment, the transfer case comprises at least one spur gear, wherein the outputs of the transfer case are so coupled to the spur gears or are formed by spur gears that the outputs are driven in the same direction.

In an alternative embodiment, the transfer case comprises at least one spur gear set whose outputs are so coupled to the spur gears or formed by spur gears that the outputs are driven in different directions of rotation.

In particular, in the execution of the hydrodynamic converter as a mating converter and in particular superimposed gearbox with different rotational direction at the input, the transfer case comprises a spur gear with two or even number of spur gears, wherein a first output of the transfer case is formed by a first spur gear and a second output of the transfer case of a opposite direction of rotation to this first spur gear driven second or further spur gear is formed. In contrast, in power transmission devices with hydrodynamic converter as a constant velocity converter, the transfer case comprise a spur gear set with three or odd number of spur gears, wherein a first output of the transfer case is formed by a first spur gear and a second output of the transfer case of a same direction of rotation to this first spur gear driven second or further spur gear is formed.

For power transmission devices of the first embodiment, the transfer case preferably comprises at least one input which forms the input of the power transmission device or is at least indirectly connected thereto in a rotationally fixed manner. The transfer case comprises at least two outputs which are arranged eccentrically to each other, wherein a first output is at least indirectly connected to the impeller of the hydrodynamic coupling and a second output is at least indirectly connected to the impeller of the hydrodynamic speed / torque converter. As a result, the torque transmission to the individual hydrodynamic components and thus power branches is realized.

According to a particularly advantageous embodiment of the input of the transfer case and the first output are arranged coaxially to each other, wherein preferably the first output is coupled to the hydrodynamic speed / torque converter, which is thus acted upon at the same speed as at the input. The hydrodynamic coupling is then connected to an eccentrically arranged to the input of the transfer case output, wherein the coupling between the input and this output is preferably realized via a translation at a slow rate. As a result, too high peripheral speeds are avoided at the connection or at the ring gear of the planetary gear. Designs with eccentric arrangement of input and power branches are also conceivable.

Depending on the requirements of the application, however, translations into the fast are possible.

With regard to the design of the transfer case itself, there are a plurality of possibilities. Preferably, the transfer case is designed as a spur gear with an odd number of spur gears, wherein the input of the power transmission device to the output of the transfer case is made coaxial and the translation between the input and the connected to the impeller of the hydrodynamic clutch output of the transfer case is designed as a translation into slow.

The hydrodynamic coupling used in the first embodiment comprises at least a pump impeller and a turbine wheel. The impeller is at least indirectly connected to the input, preferably directly or via further transmission devices, here the spur gear set, while the turbine wheel is at least indirectly connected to the output of the power transmission device, here via the superposition gear. The hydrodynamic speed / torque converter comprises at least one impeller, a turbine wheel and at least one stator. In this case, the impeller is at least indirectly coupled to the input of the power transmission device, while the turbine wheel is at least indirectly coupled to the output via the superposition gear.

When converter types are used in both embodiments preferably use constant velocity converter with adjustable pump and / or vanes. When using a counter-rotating converter, the transfer case can be reduced to straight Stirnradanzahl, in particular, a design with 2 spur gears is sufficient.

According to a particularly advantageous embodiment, the superposition gearing is arranged coaxially to one of the two power branches, in particular in the first embodiment, coaxially with one of the two hydrodynamic components. Preferably, the arrangement according to a first embodiment is coaxial with the mechanical drive or the hydrodynamic coupling, in particular coaxially with the turbine wheel of the hydrodynamic coupling. The coupling with the eccentrically arranged hydrodynamic coupling hydrodynamic speed / torque converter, in particular the turbine wheel, takes place in the simplest case via a simple spur gear. Other versions are conceivable.

According to a second alternative embodiment, it is conceivable to arrange the superposition gear coaxially with the hydrodynamic speed / torque converter.

The individual arrangement options depend essentially on the formation of the superposition gearing. This comprises in the simplest case only a planetary gear, comprising at least a first element in the form of a ring gear, a second element in the form of a web and a third element in the form of a sun gear, wherein the sun gear is coupled to the output of the power transmission device or forms. In particular, when coupling the hydrodynamic coupling with the ring gear, the first variant is particularly advantageous because the coupling with the ring gear can be realized in a simple manner, while simultaneously the connection of the hydrodynamic speed / torque converter to the web via a simple spur gear realized is.

Although in the alternative embodiment with a coaxial arrangement to the hydrodynamic speed / torque converter here also a simple connection of the web takes place, however, the drive via the ring gear is only possible via a corresponding translation.

Does the superposition gear at least one planetary gear with a first element which is at least indirectly connected to the turbine of the hydrodynamic coupling, a second element which is at least indirectly coupled to the turbine of the hydrodynamic speed / torque converter and a third element, which at least indirectly with is connected to the output of the power transmission device or forms, is formed in a particularly advantageous arrangement, the first element of the planetary gear of a ring gear, the second element of a web and the third element of a sun gear of the planetary gear.

Provided in a particularly advantageous embodiment of this further development, the hydrodynamic speed / torque converter in power flow between input and output nachordnen a brake device and vorzuordnen the superposition gear. This can be carried out as a planetary gear support of an element in execution of the superposition gear. The brake is particularly active in the first embodiment when the through connection is open and the converter is deflated, i. in the control range of the clutch.

The braking device used in the first embodiment may be embodied in various ways. This assumes the function of a parking brake device. Advantageously, this is designed as a hydrodynamic braking device. This comprises a rotor which can be coupled to the turbine wheel of the converter and a stator which is supported on a stationary component, in particular the housing. This design allows a wear-free braking and also the use of the same resource supply system as the converter and / or the hydrodynamic coupling. The hydrodynamic braking device also offers the advantage of smaller size.

An alternative embodiment consists in the design of the braking device as a mechanical braking device, in particular disc brake device, such as multi-disc brake device. The operation of these can be done mechanically, hydraulically, pneumatically, electronically or a combination of these. In hydraulic actuation can be used as the pressure medium operating medium of the hydrodynamic components. Other versions of brake devices are also conceivable.

In an advantageous development, a safety device, comprising a locking device for locking against rotation is preferably provided in addition to one of the aforementioned measures between the superposition gearing and the braking device. This locking device is designed in the simplest case as a mechanical locking device which detects the shaft relative to a stationary component, such as housing.

In principle, a multiplicity of parallel arrangements is conceivable which can be extended by additional components.

In both embodiments, it is conceivable in a development to provide a second converter in the second power branch with a different characteristic of the conversion. The advantage consists in an increase in efficiency in the speed range falling efficiency of the first converter.

In a particularly advantageous application, the use is in a drive train for driving a work machine, in particular variable-speed work machine with a drive unit, in particular drive unit with constant drive speed. The power transmission device is arranged between them in the power flow. The working machine is preferably designed as a conveying device for a fluid, in particular as a compressor, pump or centrifugal pump, boiler feed pump, while the drive unit is designed as an internal combustion engine, turbine, in particular steam or gas turbine or electric motor.

As drive units in the form of electric motors are synchronous or asynchronous motors, in particular 50 Hz or 60 Hz; 2, 4, 6 - pole design conceivable.

Possible working machines are pumps, especially: boiler feed pumps, compressors or blowers. A special field of application is the use in power plants. Here, with a parallel arrangement of the type according to the invention, the power transmission device can be provided in a simple and cost-effective manner with transmission components optimized with regard to the design, whereby optimal adaptability to the available drive machines and working machines can take place.

In an advantageous development, it is provided that the output shaft or a non-rotatably coupled thereto component is associated with a braking device. This embodiment may additionally or alternatively, i. be provided independently.

The term "wave" is to be understood functionally. This includes both the machine elements shaft, hollow shaft and rotationally symmetrical components that can take over the function of a shaft. At least indirectly connected means that the connection can be made directly or indirectly via further intermediate transmission elements, such as simple connecting elements or transmission.

This solution has the advantage that the output shaft in defined operating conditions, in particular despite the initiation of a drag torque in the power transmission device, can be completely and easily brought to a standstill and in particular can be braked by them. According to a particularly advantageous development of the output shaft or a non-rotatably coupled thereto component is associated with a device for interrupting the power flow to the working machine, which is considered downstream of the braking device in the direction of force flow from the input shaft to the output shaft. This advantageously ensures a simple, quickly realizable and complete mechanical separation between the power transmission device and the working machine and thus the drive unit and the working machine. Particularly in the case of drives of boiler feed pumps in power plant applications, this solution offers the advantage that maintenance work can be carried out on the work machine connected to the power transmission device while the drive machine is still rotating, in particular when used in power plants while the steam turbine is still rotating. Downtimes of the overall system can thus be reduced. With regard to the design of the device for interrupting the flow of power to the work machine there are a variety of possibilities. In the simplest case, this comprises a detachable connection or a release clutch. The latter can be operated manually or automatically. This can be a non-positive or positive coupling. Furthermore, this can be mechanical, hydraulic, pneumatic, electronic or a combination of these are operated. In a particularly advantageous manner, standard components can be used here. The detachable connection can be realized, for example, by releasing connecting elements between components coupled to one another or else by removing connecting parts between two components which are to be connected to one another in a rotationally fixed manner.

The braking device can be designed in various ways. This assumes the function of a parking brake device. Advantageously, this is designed as a mechanical braking device, in particular disc brake device, such as multi-disc brake device. The operation of these can be done mechanically, hydraulically, pneumatically, electronically or a combination of these. In hydraulic actuation can be used as the pressure medium operating medium of the hydrodynamic components. Other versions of brake devices are also conceivable.

In an advantageous development, a safety device, comprising a locking device for locking the output shaft against rotation, is preferably provided in addition to one of the aforementioned measures between the superposition gearing and the braking device. This locking device is designed in the simplest case as a mechanical locking device which detects the shaft relative to a stationary component, such as housing. The solution for fixing the output shaft may also be separate, i. be provided without Achschubausgleich for the converter.

• 1 zeigt beispielhaft in schematisiert vereinfachter Darstellung das Grundprinzip und die Grundfunktion einer Leistungsübertragungsvorrichtung gemäß einer ersten Ausführungsform mit Axialschubentlastungseinrichtung;
• 2 zeigt eine besonders vorteilhafte Ausbildung einer Leistungsübertragungsvorrichtung gemäß einer ersten Ausführungsform;
• 3 zeigt eine alternative zweite Ausführungsform einer Leistungsübertragungsvorrichtung mit rein mechanischem Durchtrieb in einem der Leistungszweige;
• 4 zeigt eine vorteilhafte Weiterbildung einer Leistungsübertragungsvorrichtung gemäß einer ersten Ausführungsform;
• 5 zeigt eine Ausführung einer Achschubausgleichseinrichtung.

The solution according to the invention is described below in the figures. It details the following:

• 1 shows by way of example in a schematic simplified representation of the basic principle and the basic function of a power transmission device according to a first embodiment with Axialschubentlastungseinrichtung;
• 2 shows a particularly advantageous embodiment of a power transmission device according to a first embodiment;
• 3 shows an alternative second embodiment of a power transmission device with purely mechanical drive in one of the power branches;
• 4 shows an advantageous development of a power transmission device according to a first embodiment;
• 5 shows an embodiment of a Achschubausgleichseinrichtung.

The 1 shows by way of example in a schematic highly simplified embodiment, the basic structure and the basic principle of an inventively designed power transmission device 1 to the arrangement between a here only schematically indicated drive unit 2 and a work machine 3 in a drive train 31 , The power transmission device 1 comprises at least one, at least indirectly, that is directly or via further transmission elements with the drive unit 2 coupling input e and at least one, at least indirectly, that is directly or via further transmission elements with the work machine 3 coupling output A , Between the entrance e and the exit A are a hydrodynamic coupling 4 and a hydrodynamic speed / torque converter 6 , hereinafter referred to as hydrodynamic converter, arranged. The arrangement takes place in a housing 30 ,

The entrance e or exit A is formed by components, via which the force is introduced or force discharge. These are preferably formed by waves, in particular solid or hollow shafts. However, other rotatable components which serve for coupling, such as flanges etc

The hydrodynamic coupling 4 includes at least one impeller P ₄ and a turbine wheel T ₄ , The hydrodynamic coupling 4 is a facility 5 for switching through or bridging the hydrodynamic coupling 4 assigned. This can be a so-called lock-up clutch in the simplest case. However, the bridging can also be realized elsewhere. This can be provided directly between pump and turbine or with these rotatably connected components.

The hydrodynamic converter 6 includes at least one impeller P ₆ , a turbine wheel T ₆ and at least one stator L ₆ , The hydrodynamic converter 6 It serves both the speed and torque conversion, while the hydrodynamic clutch 4 only the function of a speed converter holds. According to the invention, the hydrodynamic coupling 4 and the hydrodynamic converter 6 not coaxially arranged, but eccentric to each other in 2-power branches 7 and 8th between the entrance e and the exit A are provided and at least the respective separate power transmission via one of the power branches 7 or 8th or in power split across both, ie those two power branches 7 . 8th operated in parallel and thus the power transmission device operates with power split.

The individual pump wheels P ₄ the hydrodynamic coupling 4 and P ₆ of the hydrodynamic converter 6 are at least indirectly, that is directly or via transmission elements with the input E of the power transmission device 1 coupled. Coupled means doing a functional connection consisting of non-rotatable connections or intermediate transmission elements with or without speed / torque conversion between the input E of the power transmission device and the respective impeller P ₄ the hydrodynamic coupling or P ₆ of the hydrodynamic converter can exist. For coupling the two hydrodynamic components with the input e is a transfer case 9 provided, which the two hydrodynamic components 4 and 6 , in the power flow between input and output e . A considered, are upstream. The transfer case is with 9 referred to, in the housing 30 integrated and includes at least one input 10 which is from the input of the power transmission device e can be formed or coupled with this. The transfer case 9 further comprises at least two outputs, a first output 11 that with the hydrodynamic coupling 4 and a second exit 12 at least indirectly with the hydrodynamic converter 6 connected is. The coupling of the outputs 11 and 12 takes place in each case with the pump wheels P ₄ the hydrodynamic coupling 4 and P ₆ of the hydrodynamic converter 6 , The coupling of the turbine wheels T ₄ the hydrodynamic coupling or T ₆ of the hydrodynamic converter with the output A the power transmission device via a superposition gear 13 , This includes at least two inputs for this purpose 15 and 16 , where the first entrance 15 with the turbine wheel T ₄ the hydrodynamic coupling and the second input 16 with the turbine wheel T ₆ of the hydrodynamic converter 6 connected is. The superposition gearbox 13 further comprises at least one output 17 , either from the output A of the power transmission device 1 is formed or forms this or is connected to this, that is, at least indirectly or directly. Due to the parallel arrangement in two power branches 7 . 8th can be power transmission devices 1 be realized with a short overall length. It is also possible, depending on the requirements due to the available drive units 2 as well as the requirements and parameters to be set on the work machine 3 here by the construction of transfer case 9 and superposition gearbox 13 the power transmission device 1 optimally adapted to the given boundary conditions of the application.

The hydrodynamic coupling 4 is designed as a control clutch. This is a control device 28 assigned. This can be, for example, an adjustable scoop depending on the design of the clutch.

The 2 illustrates a particularly advantageous embodiment of a power transmission device 1 according to 1 in a schematic representation for use in power plants, especially for driving boiler feed pumps. The entrance of the transfer case 9 is coaxial with the exit 12 of the transfer case 9 , which with the hydrodynamic converter 6 is coupled, arranged. This is the power branch 8th in which the hydrodynamic converter 4 is arranged, coaxial with the input of the transfer case 9 at the same time the input E of the power transmission device 1 forms. The one with the hydrodynamic coupling 4 coupling output 11 is eccentric to the entrance 10 of the transfer case 9 arranged. In the case shown is the transfer case 9 exemplary as a spur gear 18 executed, comprising an odd number of spur gears to the same direction of rotation between the input e and the respective power branch 7 . 8th , that is hydrodynamic coupling 4 or hydrodynamic converter 6 , to ensure. The exit A the power transmission device 1 can be eccentric to both hydrodynamic components, in particular the respective turbine wheels T ₄ the hydrodynamic coupling 4 and T ₆ of the hydrodynamic converter 6 be arranged. In a particularly advantageous manner, however, the arrangement is preferably carried out coaxially with one of the hydrodynamic components, in the case shown the hydrodynamic coupling 4 , in particular the turbine wheel T ₄ the hydrodynamic coupling 4 , Regarding the formation of the superposition gear 13 There are a lot of possibilities. The 2 illustrates a particularly advantageous embodiment, comprising at least one planetary gear 14 , A first element 19 of the planetary gear 14 is with the turbine wheel T ₄ the hydrodynamic coupling 4 coupled, preferably connected directly rotatably. Other versions are conceivable. Another second element of the planetary gear 14 , herewith 20 is at least indirectly with the turbine T ₆ connected to the hydrodynamic converter, while a third element 21 of the planetary gear 14 with the exit A the power transmission device 1 is connected or forms this directly. In the case shown, the first element 19 of the planetary gear 14 from a ring gear 22 formed while the second element 20 from the jetty 23 and the third element 21 from the sun wheel 24 be formed. ring gear 22 and footbridge 23 thus form the inputs 15 and 16 of the superposition gear, while the sun gear 24 the output of the superposition gearbox 13 forms. The coupling of the bridge 23 takes place here via a simple spur gear, which reverses the direction of rotation between the turbine wheel T ₆ of the hydrodynamic converter 6 allows.

The hydrodynamic coupling 4 is with a facility 5 equipped for bridging. This is in the simplest case, a so-called lock-up clutch. This comprises a first coupling part K1 that is either with the impeller P ₄ or a rotatably coupled thereto shaft is connected and a second coupling part K2 that with the turbine wheel T ₄ or is connected to this rotatably coupled shaft. The hydrodynamic coupling 4 and the device 5 , in particular lock-up clutch form a so-called start-up and / or control unit 25 , To start and / or rules, the filling of the hydrodynamic coupling takes place 4 , About the control device 28 can the output speed at the turbine wheel T ₄ be managed. Upon reaching a certain speed, in particular synchronous speed, the device 5 for through-coupling and thus for the mechanical drive between the input e and the superposition gearbox 13 connected. About the hydrodynamic coupling 4 containing power branch 7 Thus, a constant moment is transmitted purely mechanically. The over the hydrodynamic converter 6 Achieving power share is via the spur gear 26 in the superposition gearbox 13 brought in. As for the converter 6 Typically, a flow of the working medium from the impeller arises P ₆ via at least one stator L ₆ to the turbine T ₆ , In parallel, the power from the input shaft e the power transmission device, the transfer case 9 about the direct coupling through the device 5 mechanically transmitted. The two power branches are then through the planetary gear 14 of the superposition gearbox 13 merged again and the exit A fed.

The planetary gear 14 is designed as a so-called F-gearbox. This includes, as already stated, a ring gear 22 , a sun wheel 24 as well as several on a planet carrier 23 arranged planets. In the construction shown here is now the turbine wheel T ₆ of the hydrodynamic converter 6 over the spur gear set 26 with the jetty 23 of the planetary gear 14 connected. The inventive arrangement in parallel construction of the hydrodynamic components, it is possible here the pump wheels P ₄ the hydrodynamic coupling 4 and P ₆ of the hydrodynamic converter 6 to vary supplied power or adjust the required speeds so that they are transferable from the components without damage. Due to the parallel construction, this type of power transmission device is particularly suitable for work machines, which are intended to deliver very high power and high speeds, for installation in power transmission systems for driving variable-speed machines.

In order in the operating areas where the converter 6 is emptied to ensure a support of the web is the converter 6 a braking device 27 downstream, which preferably as hydrodynamic braking device 29 is executed. This comprises a, on a stationary component, in particular housing 30 supporting the stator S and a rotationally fixed with the turbine wheel T ₆ connected rotor.

The 3 illustrates in schematic simplified representation of an embodiment according to the second embodiment, in which the power branch 7 is designed as a purely mechanical power branch with mechanical Durchtriebsanordnung. In this is no hydrodynamic coupling according to 2 furthermore also no braking device 27 required. The basic structure otherwise corresponds to the version in 2 why the same reference numbers are used for the same elements.

The statements according to 2 and 3 are here with translation into the slow for the first power branch 7 represented, in particular at drive speeds of 3000U / min. In other applications, it is also conceivable to provide a translation in quick. Furthermore, the input of the transfer case can also be arranged eccentrically to both power branches.

The 4 shows an example of an advantageous development of a power transmission device 1 according to a first embodiment. The basic structure is essentially the same as in 2 . described For identical elements, therefore, the same reference numerals are used. Incidentally, to avoid repetition, the description of the 2 directed. In this embodiment is another hydrodynamic converter 32 in the second power branch 8th intended. This comprises at least one impeller P ₃₂ , a turbine wheel T ₃₂ and a stator L ₃₂ , The second hydrodynamic converter 32 in the second power branch is designed such that it has a different characteristic of the conversion as the first transducer 6 , The advantage consists in an increase in efficiency in the speed range falling efficiency of the first converter 6 , The second converter 32 is coaxial to the first converter 6 arranged and the impeller is with the input e coupled at least indirectly. Preferably, the impeller P ₆ of the first converter 6 and P ₃₂ of the second converter 32 arranged on a common shaft. This is due to the connection shafts of the respective turbine wheels T ₆ respectively. T ₃₂ guided.

Furthermore, it is an example of the power flow from the entrance e to the exit A considered the hydrodynamic coupling 4 in the first power branch a device 34 for braking and / or setting the with the hydrodynamic coupling 4 connectable input 15 of the superposition gearbox 13 downstream. This additional brake is between turbine wheel T ₄ the hydrodynamic coupling 4 and planetary gear 13 in the first power branch 7 provided and shown here only indicated. The device 34 can be designed in various ways. Conceivable are hydrodynamic brakes or mechanical braking devices.

In 5 is a particularly advantageous embodiment of an inventively used axial thrust relief device 41 as an axial section along the longitudinal axis of a machine shaft 49 shown, the figure representation shows only one of the two halves of symmetry. The axial thrust relief device 41 is as a separate component along a machine shaft 42 arranged here, which is formed here by the turbine wheel shaft, wherein the Axialschubentlastungseinrichtung 41 Seen in the traction direction before or after the axial thrust generating machine component may be provided. A passive, self-adjusting system is used, for which two component groups which are axially displaceable relative to one another are provided, resulting in axial thrust balancing forces from an axial relative movement of the two component groups.

For the present embodiment, a on a fixed part 44 fixed thrust balance ring 43 used, at the axially on both sides of a first pressure chamber 47 and a second pressure chamber 48 connect.

The outer side surfaces of the thrust balance ring 43 thus represent the first pressure chamber 47 and the second pressure chamber 48 each one of the two side walls. The other side wall is formed by an axial side surface of a first side window 45 for the first pressure chamber 47 and a second side window 46 for the second pressure chamber 48 educated. The first side window 45 and the second side window 46 are on the machine shaft 42 attached or integrally formed with this, so that it matches the movements of the machine shaft 42 consequences. By the indicated by an arrow axial thrust move the first side window 45 and the second side window 46 synchronously in the axial direction relative to the thrust balance ring 43 , The at the front of the first side window 45 provided first labyrinth seal 57 is essentially unaffected by this axial relative movement in its sealing function. The same applies to the second labyrinth seal 58 that the second side window 46 and thus the second pressure chamber 48 assigned. Due to the thus essentially constant throttle effect by the first and the second labyrinth seal 57 . 58 , may be a pressure difference between the first pressure chamber 47 and the second pressure chamber 48 by a reciprocal opening or closing of the inflow openings to the two pressure chambers 47 . 48 respectively. This is due to the configuration of the first throttle point 52 for the first pressure chamber 47 and the second throttle 53 for the second pressure chamber 48 causes. According to the in 5 illustrated advantageous embodiment engages a disc-shaped throttle element 51 radially into an annulus 50 on, the front side of the thrust balance ring 43 is trained. This disc-shaped throttle element 51 runs with the machine shaft 42 and is therefore at an axial relative movement between the machine shaft 42 and the fixed thrust balance ring 43 a corresponding axial movement in the annulus 50 To run. Accordingly, the distance between the side walls of the disk-shaped throttle element changes 51 and the axial surfaces of the annulus 50 , The annulus 50 is by means of a feed channel 49 that is in the thrust balance ring 43 is created, supplied with pressure medium. Are at the side walls in each case a first sealing edge 54 and a second sealing edge 55 arranged, which is a small distance to the side surfaces of the disc-shaped throttle element 51 have, so create a first throttle point 52 and a second throttle 53 , due to an axial relative movement between the disc-shaped throttle element 51 and the thrust balance ring 43 reciprocally open and close. By these relative movements creates a variable pressure drop at the first throttle point 52 and the second throttle 53 , Accordingly, in an eccentric position of the disc-shaped throttle element first pressure chamber 47 and the second pressure chamber 48 to adjust. Due to the substantially same area sizes of the facing to the pressure chambers axial surfaces of the first side window 45 and the second side window 46 results from this pressure difference, an axial force, which counteracts the axial thrust. The first throttle point 52 and the second throttle 53 can be designed differently. In the present case, the sealing edges 54 and 55 the side walls of the annulus 50 assigned. Alternatively, the sealing edges on the disc-shaped throttle element 51 be arranged or the mutually facing axial side surfaces of the annular space 50 and the disc-shaped throttle element 51 can be designed to be complementary in such a way that at a relative axial movement a variable throttle effect results. According to an advantageous embodiment, the sealing edges 54 and 55 as shown in 5 as separate Components formed with the inner walls of the annulus 50 are connected. In the simplest case, this connection is effected by means of a fastening element, for example by screwing. Alternatively, a frictional connection can be created by means of a press fit.

Particularly preferred as the pressure medium, the pressurized working fluid of the transducer 6 used. For this, not in detail 5 illustrated case, a working fluid line for the hydrodynamic component, in particular converter 6 directly in connection with the feed channel 49 be set. The pressurization of the pressure medium then takes place directly through the operation of the hydrodynamic converter 6 , wherein pressure fluctuations due to the differential pressure principle do not lead to an impairment of the thrust relief. By the as a separate component at the with the hydrodynamic component 6 connected machine shaft 42 arranged Axialschubentlastungseinrichtung 41 The axial thrust can be reduced to zero, whereby the thrust bearings are relieved. Further, the axial position of the machine shaft 42 held substantially at a neutral point, being used as the pressure medium of the axial thrust relief device 41 directly the working fluid from the hydrodynamic component 6 is supplied.

The execution of 2 further shows one of the output shaft A or a non-rotatably associated with this coupled component a braking device 35 , The output shaft A or a non-rotatably coupled thereto component is further a device 36 to interrupt the flow of power to the working machine 3 assigned. This is the braking device 36 in the direction of power flow from the input shaft e to the output shaft A considered subordinate. Either the assignment of brake device takes place 35 and / or device 36 directly to the output shaft A or a non-rotatably connected to this component, for example in the form of an additional extension shaft, which may be stored for example radially or axially.

The device for interrupting the flow of power to the working machine can be designed in various ways. In the simplest case as disengaging or in the form of a connecting piece, which is detachable.

Between the superposition gearbox 13 and the facility 36 to interrupt the power flow is a safety device 37 comprising a locking device for locking the output shaft A provided against rotation. This includes, for example, socket pins, which are the output shaft A relative to a stationary component, in particular housing 30 fix.

• - Durchschaltung, d.h. schaltbare Kupplung 5 öffnen;
• - Hydrodynamische Kupplung 25 entleeren (Schöpfrohr auf 0%); oder Wandler 6 entleeren
• - minimale Drehzahl der Arbeitsmaschine
• - Bremseinrichtung 35 auf der Ausgangswelle A aktivieren und den Abtrieb komplett zum Stillstand bringen
• - Verriegelungseinrichtung 37 aktivieren, insbesondere einen Steckbolzen zur zusätzlichen mechanischen Blockierung einbauen
• - Einrichtung 36, hier aktivieren, beispielsweise ein Verbindungsstück zwischen Vorecon-Abtrieb und Arbeitsmaschine 3 ausbauen, damit eine komplette mechanische Trennung vorhanden ist. Die Lösung zum Festsetzen der Ausgangswelle A kann auch bei einer Ausführung gemäß 2 frei von der Verwendung eines Achsschubausgleich erfolgen. ferner kann die Lösung zum Festsetzen der Ausgangswelle A auch bei allen anderen Konfigurationen, insbesondere den in den 1, 3 und 4 dargestellten Konfigurationen eingesetzt werden.

For safe shutdown of the output shaft A the procedure is as follows:

• - Through, ie switchable coupling 5 to open;
• - Hydrodynamic coupling 25 empty (scoop to 0%); or transducer 6 empty
• - minimum speed of the working machine
• - Braking device 35 Activate on the output shaft A and bring the output completely to a standstill
• - Locking device 37 activate, in particular a plug pin for additional mechanical blocking install
• - Facility 36 , Activate here, for example, a connector between Vorecon output and work machine 3 Remove for complete mechanical separation. The solution for fixing the output shaft A can also be used in a version according to 2 free from the use of an axial thrust compensation. Further, the solution for fixing the output shaft A also with all other configurations, in particular those in the 1 . 3 and 4 illustrated configurations are used.

The 2 further clarifies the arrangement and location of the supply pumps 38 and 39 for the converter 6 and the hydrodynamic coupling 4 , In the case illustrated, these are in the installed position to the left of the respective hydrodynamic component 4 . 6 arranged. The drive is via a with the respective impeller shaft of the impellers P6 respectively. P4 coupled translation, in particular a corresponding spur gear 59 . 60 , By broken line is an alternative arrangement for the hydrodynamic coupling 4 shown. The supply pump 39 is in this case then right of the hydrodynamic coupling 4 arranged and with the impeller shell on this side or coupled to the impeller shell coupling part K1 the coupling device 5 about the translation level 60 ' coupled.

The embodiments according to the invention of a power transmission device can be used in particular in power plants in drive trains between a drive unit, in particular at a constant speed and a variable-speed work machine. Particularly preferred applications are the use between a steam or gas turbine and a boiler feed pump. As a power plant, no additional electric motor is required and the drive system is efficient, since no conversion of steam into electricity and mechanical energy is required.

LIST OF REFERENCE NUMBERS

1

Power transmission device

2

power unit

3

working machine

4

hydrodynamic coupling

5

Device for switching through or bridging

6

hydrodynamic speed / torque converter, in particular hydrodynamic converter

7

power branch

8th

power branch

9

Transfer Case

10

Entrance of the transfer case

11

Output of the transfer case

12

Output of the transfer case

13

Superposition gear

14

planetary gear

15

Input of the superposition gearbox

16

Input of the superposition gearbox

17

Output of the superposition gearbox

18

spur gear

19

first element of the planetary gear

20

second element of the planetary gear

21

third element of the planetary gear

22

ring gear

23

web

24

sun

25

Starting and / or regulating device

26

spur gear

27

braking means

28

Control device / scoop tube

29

hydrodynamic brems

30

casing

31

powertrain

32

second hydrodynamic speed / torque converter

32

connecting shaft

34

Device for braking and / or setting the input of the superposition gearing which can be connected to the hydrodynamic coupling

35

braking means

36

Device for interrupting the flow of power to the working machine 3

37

locking device

38

supply pump

39

supply pump

41

Achsschubentlastungseinrichtung

42

machine shaft

43

Thrust balance ring

44

fixed part

45

first side window

46

second side window

47

first pressure chamber

48

second pressure chamber

49

feed channel

50

annulus

51

disc-shaped throttle element

52

first throttle point

53

second throttle point

54

first sealing edge

55

second sealing edge

56

axial thrust

57

first labyrinth seal

58

second labyrinth seal

59, 59 '

spur gear

60, 60 '

spur gear

K1, K2

coupling part

S

stator

R

rotor

P ₄

impeller

T ₄

turbine

P ₆

impeller

T ₆

turbine

L

stator

P ₃₂

impeller

T ₃₂

turbine

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 3441877 A1 [0002]
• DE 102008034607 [0002]
• WO 2016/012317 A1 [0003]

Claims (21)

Power transmission device (1) with a housing (30), with at least one, with a drive unit (2) connectable input (E) and, at least indirectly connectable to a working machine (3) output (A), with a force flow between the input (E) and the output (A) arranged first mechanical power branch (7) and a further second, a hydrodynamic speed / torque converter (6) comprising the second power branch (8) comprising at least one impeller (P ₆ ), a turbine wheel (T ₆ ) and a stator (L), wherein the two power branches (7, 8) to the output (A) via a superposition gear (13) are connectable; first and second power branches (7, 8) are arranged parallel to one another and can be connected or connected to the input (E) of the power transmission device (1) via a transfer case (9) arranged in the housing (30); first and second power branches (7, 8) can be connected or connected to the output (A) of the power transmission device (1) via a summing gear arranged in the housing (30); the shaft carrying the turbine wheel of the hydrodynamic speed / torque converter is mounted via at least one bearing in the housing (30); characterized in that between the turbine wheel of the hydrodynamic speed / torque converter (6) and the bearing a Achsschubentlastungseinrichtung is arranged. Power transmission device (1) according to Claim 1 , characterized in that the hydrodynamic speed / torque converter (6) considered in the power flow from the input (E) to the output (A) means (27) for braking and / or setting of the hydrodynamic speed / torque converter (6) connectable Input (16) of the superposition gear (13) is arranged downstream and the Achsschubentlastungseinrichtung between the turbine of the hydrodynamic speed / torque converter (6) and the means (27) for braking and / or setting of the hydrodynamic speed / torque converter (6) connectable Input (16) of the superposition gear (13) is arranged. Power transmission device (1) according to one of Claims 1 or 2 , characterized in that the hydrodynamic speed / torque converter has a supply channel for supplying working fluid to the working space and the Achsschubentlastungseinrichtung at least one, over at least one pressure medium fillable pressure chamber acted upon relief element for applying a counterforce to the thrust on the shaft, wherein the pressure chamber with the Filling channel of the hydrodynamic speed / torque converter is coupled. Power transmission device (1) according to Claim 1 to 3 characterized in that the axial thrust relief device (40) comprises: a thrust balance ring (43) having a supply channel (49) for a pressure medium formed therein opening into an annular space (50) at the end of the thrust balance ring (43); a first side window (45) and a second side window (46) each axially adjacent and disposed on opposite sides of the thrust balance ring (3) to form a first pressure chamber (47) and a second pressure chamber (48) Pressure chamber (47) and the second pressure chamber (48) are each downstream on a labyrinth seal (57, 58) are completed and upstream on a first throttle point (52) for the first pressure chamber (47) and a second throttle point (53) for the second pressure chamber (48) in each case a connection to the annular space (50) for the influx of pressure medium consists; a disk-shaped throttle element (51) engaging in the annular space (10); the thrust balance ring (43) and the throttle element (51) are arranged so that one of the two components is fixed in the axial direction and the other component follows an axial movement of the associated machine shaft (42), wherein axial relative movement between the thrust balance ring (43) and the Throttling element (51) the first throttle point (42) and the second throttle point (43) are reciprocally opened and closed, so that between the first pressure chamber (47) and the second pressure chamber (48) creates a pressure difference. Power transmission device (1) according to one of Claims 1 to 4 ; characterized in that the first power branch (7) comprises a hydrodynamic coupling (4) comprising at least one impeller (P) and a turbine wheel (T). Power transmission device (1) according to Claim 5 , characterized in that the hydrodynamic coupling (4) is designed as a control clutch, in particular as a hydrodynamic clutch with adjustable scoop. Power transmission device (1) according to one of Claims 1 to 6 , characterized in that a device (5) for switching through or bridging the hydrodynamic coupling (4) is provided for the realization of a mechanical drive through. Power transmission device (1) according to any one of the preceding claims, characterized in that the hydrodynamic coupling (4) and the hydrodynamic speed / torque converter (6) viewed in the installation position viewed in the axial direction between input (E) and output (A) free of offset or are arranged with an offset. Power transmission device (1) according to one of Claims 1 to 4 , characterized in that the first mechanical power indicator (7) is free of further speed and / or torque converter devices, in particular designed as a mechanical drive arrangement and the second power branch (8) free of addition to the hydrodynamic speed / torque converter (6) provided speed and / or torque converter devices. Power transmission device (1) according to one of Claims 1 to 9 , characterized in that the first and second power branch is free of further speed and / or torque converter means. Power transmission device (1) according to one of the preceding claims, characterized in that a device (32) for braking and / or setting of the hydrodynamic coupling (4) connectable input (15) of the superposition gear (13) is provided and this means (32 ) and / or device (27) for braking and / or setting the input (16) of the superposition gearing (13) which can be connected to the hydrodynamic speed / torque converter (6) is designed as a braking device selected from the following group of braking devices: hydrodynamic braking device (29) - mechanical braking device, in particular disc or multi-disc brake - parking brake Power transmission device (1) according to any one of the preceding claims, characterized in that the transfer case (9) comprises at least one input (10) which forms the input (E) of the power transmission device (1) or at least indirectly connected to this non-rotatably and the Transfer case (9) comprises at least two outputs (11, 12) which are arranged eccentrically to one another, wherein a first output to the first power branch (7) and / or the impeller (P ₄ ) of the hydrodynamic coupling (4) is at least indirectly connected and a second output (12) is at least indirectly connected to the impeller (P ₆ ) of the hydrodynamic speed / torque converter (6). Power transmission device (1) according to Claim 12 characterized in that the input (10) of the transfer case (9) is arranged coaxially or eccentrically to an input of one of the power branches (7, 8), the input being from an impeller (P ₄ , P ₆ ) of one of the hydrodynamic components (9). 4, 6) or a shaft of the mechanical drive-through arrangement is formed. Power transmission device (1) according to one of the preceding claims, characterized in that the summing gear (13) is coaxial with one of the power branches (7, 8); the hydrodynamic components (4, 6) - hydrodynamic coupling (4) or hydrodynamic speed / torque converter (6) - is arranged and the coupling of the output (A) of the other hydrodynamic component (6, 4) with the summation gear (13) via a connecting gear. Power transmission device (1) according to one of the preceding claims, characterized in that the summing gear (13) comprises at least one planetary gear (14), with a first element (19) which at least indirectly with the turbine wheel (T ₄ ) of the hydrodynamic coupling (4 ), a second element (20) which is at least indirectly coupled to the turbine wheel (T ₆ ) of the hydrodynamic speed / torque converter (6) and a third element (17) which at least indirectly with the output (A) of Power transmission device (1) is connected or forms, wherein that the first element (19) of the planetary gear (14) by a ring gear (22) is formed, the second element (20) of a web (23) and the third element (21 ) of a sun gear (24) of the planetary gear (14). Power transmission device (1) according to one of Claims 8 to 15 , characterized in that the transfer case (9) comprises at least one spur gear and the outputs of the transfer case are so coupled to the spur gears or are formed by spur gears that the outputs (11, 12) of the transfer case (9) are driven in the same direction or in that the transfer case (9) comprises at least one spur gear set and the outputs (11, 12) of the transfer case (9) are coupled to the spur gears or formed by spur gears so that the outputs are driven in different directions of rotation. Power transmission device (1) according to one of Claims 8 to 16 , characterized in that the hydrodynamic converter (6) is designed as a counter-rotating converter and the transfer case (9) has a spur gear set with two or straighter Number of spur gears comprises, wherein a first output (11) of the transfer case (9) is formed by a first spur gear and a second output (12) of the transfer case (9) formed by a opposite direction of rotation to this first spur second or further spur gear becomes. Power transmission device (1) according to one of Claims 10 to 17 , characterized in that the hydrodynamic converter (6) is designed as a constant velocity converter and the transfer case (9) comprises a spur gear set with three or odd number of spur gears, wherein a first output (11) of the transfer case (9) is formed by a first spur gear and a second output (12) of the transfer case (9) is formed by a driven with the same direction of rotation to this first spur second or further spur gear. Power transmission device (1) according to one of the preceding claims, characterized in that in the second power branch, a further second hydrodynamic speed / torque converter (32) is provided, which is arranged coaxially to the hydrodynamic speed / torque converter (6), wherein the second hydrodynamic speed - / torque converter (32) has a different characteristic of the conversion, as the first converter (6) and each converter can be used in different operating ranges. Drive train (31) for driving a work machine (3), in particular variable-speed work machine with a drive unit (2), in particular drive unit with a constant drive speed of a power transmission device (1) according to one of Claims 1 to 20 , wherein the working machine (3) is designed as a conveying device for a fluid, in particular as a compressor, pump or centrifugal pump, boiler feed pump. Drive train (31) after Claim 19 , Characterized in that the drive unit (2) is designed as an element selected from the group mentioned below elements: - Turbine, in particular steam turbine or gas turbine; - electric motor; - Combustion engine - as a combined unit of a turbine and an electric motor.

Images