Force transmission device in particular for power transmission between a drive engine and an output

Abstract

A force transmission device, in particular or power transmission between a drive engine and an output, comprising a damper assembly with at least two dampers, which can be connected in series, and a rotational speed adaptive absorber, wherein the rotational speed adaptive tuned mass damper is disposed between the dampers at least in one force flow direction through the force transmission device.

Claims

.[. .[.1. A force transmission device for power transmission between a drive engine and an output, comprising: a damper assembly with first and second dampers, which can be connected in series; and a rotational speed adaptive absorber, wherein the rotational speed adaptive absorber is disposed between the first and second dampers at least in one force flow direction through a force transmission device, wherein each of the first and second dampers includes a primary component and a secondary component, and wherein the primary component of the second damper is connected torque proof with the secondary component of the first damper..]. .].

.[. .[.2. The force transmission device according to claim 1, comprising: a hydrodynamic component with at least one primary shell functioning as a pump shell (P) and a secondary shell functioning as a turbine shell (T), forming an operating cavity (AR) with one another, wherein the turbine shell (T) is connected at least indirectly torque proof with an output (A) of the force transmission device, and a coupling is performed through at least one of the first and second dampers of the damper assembly, and wherein the rotational speed adaptive absorber is connected at least indirectly torque proof with the secondary shell..]. .].

.[. .[.3. The force transmission device according to claim 2, wherein the rotational speed adaptive absorber is connected directly torque proof with the secondary shell (SR)..]. .].

.[. .[.4. The force transmission device according to claim 2, wherein the rotational speed adaptive absorber is connected with an element of the damper assembly, and the element is connected torque proof with the secondary shell of the hydrodynamic component..]. .].

.[. .[.5. The force transmission device according to claim 4, wherein the rotational speed adaptive absorber is connected with an element of a damper of the damper assembly, and the element is connected directly torque proof with the secondary shell of the hydrodynamic component..]. .].

.[. .[.6. The force transmission device according to claim 4, wherein the rotational speed adaptive absorber is coupled with an element of a damper, the element of the damper is connected with an element of another damper of the damper assembly, and the element of the another damper is directly connected with the secondary shell of the hydrodynamic component..]. .].

.[. .[.7. The force transmission device according to claim 2, wherein the hydrodynamic component is configured as a hydrodynamic speed-/torque converter comprising at least one stator shell (L)..]. .].

.[. .[.8. The force transmission device according to claim 2, wherein the hydrodynamic component is configured as a hydrodynamic clutch without a stator shell (L)..]. .].

.[. .[.9. The force transmission device according to claim 1, comprising: a device for at least partially bridging the power transmission through the hydrodynamic component, wherein the device is connected with an output (A) of the force transmission device through at least one damper of the damper assembly..]. .].

.[. .[.10. The force transmission device according to claim 1, wherein the damper assembly is disposed in a force flow between an input (E) and the output (A) in series with a hydrodynamic component and a device for bridging the hydrodynamic component..]. .].

.[. .[.11. The force transmission device according to claim 1, wherein the damper assembly is configured to be disposed in the force flow at least in series with a hydrodynamic component..]. .].

.[. .[.12. The force transmission device according to claim 11, wherein the respective other component, the device or the hydrodynamic component is coupled to the damper assembly through the connection of the first and second dampers..]. .].

.[. .[.13. The force transmission device according to claim 1, wherein the damper assembly is configured to be disposed in the force flow at least in series with a device for bridging a hydrodynamic component..]. .].

.[. .[.14. The force transmission device according to claim 1, wherein the first and second dampers of the damper assembly are configured as series or parallel dampers, comprising damper component assemblies..]. .].

.[. .[.15. The force transmission device according to claim 14, wherein the damper component assemblies of a damper are disposed on a common diameter..]. .].

.[. .[.16. The force transmission device according to claim 14, wherein the damper component assemblies of a damper are disposed on different diameters..]. .].

.[. .[.17. The force transmission device according to claim 1, wherein at least one of the first and second dampers is configured as a single damper..]. .].

.[. .[.18. The force transmission device according to claim 17, wherein the first and second dampers are disposed offset to one another in radial direction..]. .].

.[. .[.19. The force transmission device according to claim 1, wherein the first and second dampers are disposed offset relative to one another in axial direction..]. .].

.[. .[.20. The force transmission device according to claim 1, wherein the rotational speed adaptive absorber is configured as centrifugal force pendulum device, comprising at least one inertial mass support device and at least one inertial mass, which are supported at the inertial mass support device, movable relative thereto in radial direction. so that they can perform a pendulum type motion..]. .].

.[. .[.21. The force transmission device according to claim 1, wherein the rotational speed adaptive absorber is disposed and viewed in axial direction, spatially between an input (E) and the output (A) of the force transmission device, between the damper assembly and a hydrodynamic component..]. .].

.[. .[.22. The force transmission device according to claim 1, wherein the rotational speed adaptive absorber is disposed in axial direction spatially between the first and second dampers..]. .].

.[. .[.23. The force transmission device according to claim 1, wherein the rotational speed adaptive absorber is disposed in axial direction spatially between an input (E) and the output (A) of the force transmission device in front of the first and second dampers of the damper assembly..]. .].

.[. .[.24. The force transmission device according to claim 1, wherein inertial masses are disposed in radial direction in a portion of an extension of the damper assembly..]. .].

25. The force transmission device according to claim 1, wherein each of the first and second dampers comprise at least one primary component and one secondary component, and wherein the primary component or the secondary component are formed either by a flange element, or by drive disks disposed on both sides of the flange elements, are disposed coaxially relative to one another, are rotatable relative to one another in circumferential direction, and are coupled with one another through torque transmission devices and damping coupling devices.

.[. .[.26. The force transmission device according to claim 1, wherein components of the absorber form an integral unit with components of a connection element, in particular of a damper of the damper assembly or with a secondary shell, or are integrally configured therewith..]. .].

.[. .[.27. The force transmission device according to claim 1, wherein a damper of the damper assembly is configured as a mechanical damper..]. .].

.[. .[.28. The force transmission device according to claim 1, wherein a damper of the damper assembly is configured as a combined mechanical hydraulic damper..]. .].

.[. .[.29. The force transmission device according to claim 1, wherein the rotational speed adaptive absorber is configured for an order of an excitation of a drive unit, in particular the drive engine, and wherein a centrifugal force influence upon a particular inertial mass, which is reduced by a centrifugal oil pressure, is considered by configuring it for an order that is higher by >0.05 to 0.5 than without the centrifugal oil pressure..]. .].

.Iadd.30. A force transmission device for power transmission between a drive engine and a transmission input shaft, comprising: an output connected to the transmission input shaft; a damper assembly that includes first and second dampers connected in series; and a rotational speed adaptive absorber, wherein the rotational speed adaptive absorber is disposed between the first and second dampers at least in one force flow direction through the force transmission device, wherein a resonance frequency of the rotational speed adaptive absorber is proportional to a rotational speed of the drive engine, wherein each of the first and second dampers includes an elastic element, a primary component, and a secondary component, wherein the primary component of the second damper is connected torque proof with the secondary component of the first damper, wherein the elastic element of the first damper is offset from the elastic element of the second damper in a direction of the rotational axis of the force transmission device, wherein the rotational speed adaptive absorber includes pairs of inertial masses, is connected torque proof with the secondary component of the first damper, and is integral with a component of the second damper, wherein the rotational speed adaptive absorber further includes an inertial mass support device to which the pairs of inertial masses are connected, wherein proximal ends of at least one pair of inertial masses of the pairs of inertial masses are more proximal to the rotational axis of the force transmission device, in radial direction, than a center of the elastic element of the first damper, when viewed in a cross-section along the rotational axis of the force transmission device, wherein the pairs of inertial masses are movable with respect to the inertial mass support device, and wherein the primary component of the second damper receives a dampened rotational force from the secondary component of the first damper..Iaddend.

.Iadd.31. The force transmission device according to claim 30, wherein the secondary component of the first damper and the primary component of the second damper form an integral unit..Iaddend.

.Iadd.32. The force transmission device according to claim 30, wherein the inertial mass support device has an annular disc shape, and wherein inertial masses of each pair of inertial masses are disposed on different sides of the inertial mass support device..Iaddend.

.Iadd.33. The force transmission device according to claim 30, wherein the output of the force transmission device is a hub configured to connect the force transmission device to the transmission input shaft, and wherein the secondary component of the second damper is configured to transfer a dampened rotational force that has been dampened by the first damper, the second damper, and the rotational speed adaptive absorber to the hub..Iaddend.

.Iadd.34. The force transmission device according to claim 30, wherein the elastic element of each of the first damper and the second damper comprises a spring..Iaddend.

.Iadd.35. The force transmission device according to claim 34, wherein distal ends of at least one pair of inertial masses are more distal to the rotational axis of the force transmission device, in a radial direction, than a distal end of the elastic element of the first damper when viewed in a cross-section along the rotational axis of the force transmission device..Iaddend.

.Iadd.36. The force transmission device according to claim 30, wherein the primary component of the first damper is configured as a disc shaped element and the secondary component of the second damper is configured as a disc shaped element..Iaddend.

.Iadd.37. The force transmission device according to claim 30, further comprising a turbine shell, wherein the primary component of the second damper is connected torque proof with the turbine shell..Iaddend.

.Iadd.38. A force transmission device for power transmission between a drive engine and a transmission input shaft, comprising: an output connected to the transmission input shaft; a damper assembly that includes first and second dampers connected in series; and a rotational speed adaptive absorber, wherein the rotational speed adaptive absorber is disposed between the first and second dampers at least in one force flow direction through the force transmission device, wherein a resonance frequency of the rotational speed adaptive absorber is proportional to a rotational speed of the drive engine, wherein each of the first and second dampers includes an elastic element, a primary component, and a secondary component, wherein the primary component of the second damper and the secondary component of the first damper form an integral unit, wherein the elastic element of the first damper is offset from the elastic element of the second damper in a direction of the rotational axis of the force transmission device, wherein the primary component of the second damper receives a dampened rotational force from the secondary component of the first damper, wherein the rotational speed adaptive absorber includes a plurality of inertial masses, each configured to perform pendulum type motion, wherein the rotational speed adaptive absorber further includes an inertial mass support device to which the plurality of inertial masses are connected, wherein a proximal end of at least one of the plurality of inertial masses is more proximal to the rotational axis of the force transmission device, in a radial direction, than a center of the elastic element of the first damper, when viewed in a cross-section along the rotational axis of the force transmission device, wherein the inertial masses are movable relative to the inertial mass support device to perform the pendulum type motion, and wherein the rotational speed adaptive absorber is connected torque proof with the integral unit that forms the primary component of the second damper and the secondary component of the first damper..Iaddend.

.Iadd.39. The force transmission device according to claim 38, wherein the torque proof connection between the integral unit and the rotational speed adaptive absorber is provided by a cylindrical shaped element..Iaddend.

.Iadd.40. The force transmission device according to claim 38, wherein the output of the force transmission device is a hub configured to connect the force transmission device to the transmission input shaft, and wherein the secondary component of the second damper is configured to transfer a dampened rotational force that has been dampened by the first damper, the second damper, and the rotational speed adaptive absorber to the hub..Iaddend.

.Iadd.41. The force transmission device according to claim 38, wherein the inertial mass support device has an annular disc shape, and wherein the plurality of inertial masses include inertial masses disposed on one side of the inertial mass support device and inertial masses disposed on the other side of the inertial mass support device..Iaddend.

.Iadd.42. The force transmission device according to claim 41, wherein the elastic element of the first damper is a first spring, and the elastic element of the second damper is a second spring..Iaddend.

.Iadd.43. The force transmission device according to claim 42, wherein the plurality of inertial masses are disposed at a greater distance, in a radial direction extending from a rotational axis of the force transmission device, than the first spring..Iaddend.

.Iadd.44. The force transmission device according to claim 43, wherein the plurality of inertial masses are disposed at a greater distance, in a radial direction extending from a rotational axis of the force transmission device, than the second spring..Iaddend.

.Iadd.45. The force transmission device according to claim 42, wherein the primary component of the first damper is configured as a disc shaped element and the secondary component of the second damper is configured as a disc shaped element..Iaddend.

.Iadd.46. A force transmission device for power transmission between a drive engine and a transmission input shaft, comprising: an output connected to the transmission input shaft; a damper assembly that includes first and second dampers connected in series; and a rotational speed adaptive absorber, wherein the rotational speed adaptive absorber is disposed between the first and second dampers at least in one force flow direction through the force transmission device, wherein a resonance frequency of the rotational speed adaptive absorber is proportional to a rotational speed of the drive engine, wherein each of the first and second dampers includes an elastic element, a primary component, and a secondary component, wherein the primary component of the second damper is connected torque proof with the secondary component of the first damper, wherein the elastic element of the first damper is offset from the elastic element of the second damper in a direction of the rotational axis of the force transmission device, wherein the rotational speed adaptive absorber includes four pairs of inertial masses and is connected torque proof with the secondary component of the first damper and the primary component of the second damper, wherein each of the plurality of inertial masses is configured to perform pendulum type motion, wherein proximal ends of at least one pair of inertial masses of the four pairs of inertial masses are more proximal to the rotational axis of the force transmission device, in radial direction, than a center of the elastic element of the first damper, when viewed in a cross-section along the rotational axis of the force transmission device, wherein the force transmission device is arranged such that, when operated, the pairs of inertial masses are influenced by centrifugal oil pressure force, and wherein the rotational speed adaptive absorber is tuned higher by >0.05 to 0.5 as compared to tuning for an order of an excitation of the drive engine in the absence of centrifugal oil pressure..Iaddend.

.Iadd.47. The force transmission device according to claim 46, wherein the secondary component of the first damper and the primary component of the second damper form an integral unit..Iaddend.

.Iadd.48. The force transmission device according to claim 47, wherein the integral unit is connected torque proof to the rotational speed adaptive absorber..Iaddend.

.Iadd.49. The force transmission device according to claim 48, wherein the integral unit is connected torque proof to the rotational speed adaptive absorber using a cylindrical shaped element..Iaddend.

.Iadd.50. The force transmission device according to claim 48, wherein the rotational speed adaptive absorber further includes an inertial mass support device to which the four pairs of inertial masses are connected..Iaddend.

.Iadd.51. The force transmission device according to claim 48, wherein the output of the force transmission device is a hub configured to connect the force transmission device to the transmission input shaft, and wherein the secondary component of the second damper is configured to transfer a dampened rotational force that has been dampened by the first damper, the second damper, and the rotational speed adaptive absorber to the hub..Iaddend.

.Iadd.52. The force transmission device according to claim 48, wherein the elastic element of the first damper is a first spring, and the elastic element of the second damper is a second spring, and wherein the four pairs of inertial masses are disposed at a greater distance, in a radial direction extending from a rotational axis of the force transmission device, than the first spring and the second spring..Iaddend.

.Iadd.53. The force transmission device according to claim 52, wherein the primary component of the first damper is configured as a disc shaped element and the secondary component of the second damper is configured as a disc shaped element..Iaddend.

.Iadd.54. A force transmission device for power transmission between a drive engine and a transmission input shaft, comprising: an output; a damper assembly that includes first and second dampers connected in series; a rotational speed adaptive absorber comprising four pairs of inertial masses; and a hydrodynamic component with at least one primary shell functioning as a pump shell (P) and a secondary shell functioning as a turbine shell (T), forming an operating cavity (AR) with one another, wherein the rotational speed adaptive absorber includes an inertial mass support device to which the pairs of inertial masses are connected, wherein the rotational speed adaptive absorber is connected torque proof with the secondary shell via the inertial mass support device, wherein the rotational speed adaptive absorber is disposed between the first and second dampers at least in one force flow direction through the force transmission device, wherein a resonance frequency of the rotational speed adaptive absorber is proportional to a rotational speed of the drive engine, wherein each of the first and second dampers includes an elastic element, a primary component, and a secondary component, wherein the elastic element of the first damper is offset from the elastic element of the second damper in a direction of the rotational axis of the force transmission device, wherein the primary component of the second damper is connected torque proof with the secondary component of the first damper, wherein the turbine shell (T) is connected torque proof with the primary component of the second damper, wherein proximal ends of at least one pair of inertial masses of the four pairs of inertial masses are more proximal to the rotational axis of the force transmission device, in radial direction, than a center of the elastic element of the first damper, when viewed in a cross-section along the rotational axis of the force transmission device, wherein the rotational speed adaptive absorber is connected torque proof with the secondary component of the first damper and the primary component of the second damper, and wherein each of the plurality of inertial masses is configured to perform pendulum type motion..Iaddend.

.Iadd.55. The force transmission device according to claim 54, wherein the secondary component of the first damper and the primary component of the second damper form an integral unit..Iaddend.

.Iadd.56. The force transmission device according to claim 55, wherein the elastic element of the first damper is a first spring, and the elastic element of the second damper is a second spring..Iaddend.

.Iadd.57. The force transmission device according to claim 56, wherein the four pairs of inertial masses are disposed at a greater distance, in a radial direction extending from a rotational axis of the force transmission device, than the first and second springs..Iaddend.

.Iadd.58. The force transmission device according to claim 57, wherein the primary component of the first damper is configured as a disc shaped element and the secondary component of the second damper is configured as a disc shaped element..Iaddend.

Description

BRIEF DESCRIPTION OF THE DRAWINGS

(1) The solution according to the invention is subsequently described with reference to drawing figures:

(2) FIGS. 1a-1d illustrate possible basic configurations of force transmission devices with a functional disposition of rotational speed adaptive absorbers in a simplified schematic illustration;

(3) FIG. 2 illustrates a first embodiment of a force transmission device configured according to the invention with reference to an axial sectional view;

(4) FIG. 3 illustrates a second embodiment of a force transmission device configured according to the invention with reference to an axial sectional view;

(5) FIG. 4 illustrates an exemplary embodiment of a rotational speed adaptive absorber in a view from the right;

(6) FIG. 5 illustrates an option for directly coupling the rotational speed adaptive absorber with the turbine shell;

(7) FIGS. 6a-6d illustrate possible configurations of damper assemblies providing connection options for a rotational speed adaptive absorber; and

(8) FIG. 7 illustrates the advantages of the solution according to the invention over an embodiment without a rotational speed adaptive absorber with reference to a diagram.

DETAILED DESCRIPTION OF THE INVENTION

(9) FIG. 1a illustrates the basic configuration of a force transmission device according to the invention in a simplified schematic depiction for power transmission in particular in drive trains of vehicles. Thus, the force transmission device 1 is used for power transmission between a drive engine 100 which can, for example, be configured as a combustion engine and an output 101. The force transmission device 1 includes at least an input E and an at least an output A. The input E is thus connected to the drive engine 100 at least indirectly, the output A is thus connected at least indirectly with the units 101 to be driven, for example, in the form of a transmission. “At least indirectly” thus means that the coupling is either performed directly, this means without additional transmission elements disposed therebetween, or indirectly through additional transmission elements. The terms “input” and “output” are thus to be interpreted in a functional manner in force flow direction from a drive engine to an output and they are not limited to particular configurative details of embodiment.

(10) The force transmission device 1 includes a damper assembly 2 which is disposed between the input E and the output A. The damper assembly 2 includes at least two dampers 3 and 4 which can be connected in series which form damper stages and a rotational speed adaptive absorber 5. A rotational speed adaptive absorber 5 is thus interpreted as a device for absorbing variations in rotational speed, the device not transmitting power, but configured to absorb rotational vibrations over a larger range of rotational speeds, advantageously over the entire range of rotational speeds, in that inertial masses tend to move in a circular path with a maximum distance about the torque induction axis due to a centrifugal force. The rotational speed adaptive absorber 5 is thus formed by a centrifugal force pendulum device. The resonance frequency of the absorber 5 is thus proportional to the speed of the exciting unit, in particular of the drive engine 100. The superposition of the rotation through rotational vibrations leads to a pendulum type relative movement of the inertial masses. According to the invention the rotational speed adaptive absorber 5 is connected in the force flow in at least one of the theoretically possible force flow directions viewed over the damper assembly 2 between the two dampers 3 and 4 of the damper assembly 2. Besides damping vibrations through the particular dampers 3 and 4, the rotational speed adaptive absorber 5 thus operates at different frequencies.

(11) There is a plurality of options for the embodiment of the dampers 3 and 4 of the damper assembly 2 and their connection in force transmission devices 1 with additional components. Thus, in particular for embodiments with a hydrodynamic component 6 and a device 7 for at least partially locking up the hydrodynamic component, a differentiation is made between embodiments with a series connection of the dampers 3 and 4 with respect to their function as an elastic clutch, this means torque transmission and damping in both power paths or at least for a power transmission through one of the components with a series connection of the dampers 3, 4 as elastic clutches and a power transmission through the other component with one of the dampers 3 or 4 acting as an elastic clutch and the other damper 3 or 4 acting as an absorber.

(12) FIG. 1b illustrates a particularly advantageous embodiment of the force transmission device 1 with a damper assembly 2 with an integrated rotational speed adaptive absorber 5, including at least a hydrodynamic component 6 and a device 7 for at least partially circumventing the force transmission through the hydrodynamic component 6. The hydrodynamic component 6 includes at least one primary shell functioning as a pump shell P when coupling with the input E and for a force flow direction from the input E to the output A and a secondary shell coupled at least indirectly with the output A torque proof and functioning as a turbine shell T for a power transmission from the input E to the output A, the pump shell P and the turbine shell T forming an operating cavity AR. The hydrodynamic component 6 can be configured as a hydrodynamic clutch which provides speed conversion or it can be configured in a particularly advantageous embodiment as a hydrodynamic speed-/torque converter wherein the power transmission through the hydrodynamic speed-/torque converter always provides a torque and moment conversion. In this case the hydrodynamic component 6 includes at least another so called stator shell L, which can either be supported fixed in place or rotatable depending on the embodiment. The stator shell L can furthermore be supported at a freewheeling clutch. Thus, the hydrodynamic component 6 is disposed between the input E and the output A. This describes a first power path I in the force flow between the input E and the output A viewed over the hydrodynamic component 6. The device 7 for bridging the hydrodynamic component 6 is advantageously provided in the form of a so called lock up clutch which is an actuatable clutch device in the simplest case. The clutch device can be configured as a synchronously actuatable clutch device typically; however, it is configured as a friction clutch preferably in disc configuration. The clutch device is also disposed between the input E and the output A and defines a second power path when power is transmitted through the clutch device in which the power transmission is performed mechanically. Thus, the damper assembly 2 is disposed behind the device 7 in force flow direction from the input E to the output A and furthermore disposed behind the hydrodynamic component 6. The rotational speed adaptive absorber 5 is thus disposed subsequent to the hydrodynamic component 6 and also subsequent to the mechanical clutch in force flow direction from the input E to the output A. This is implemented in that the rotational speed adaptive absorber 5 configured as a centrifugal force pendulum is connected at least indirectly torque proof with the secondary shell of the hydrodynamic component 6 functioning as a turbine shell T in at least one operating state and it is furthermore connected with the output of the device 7.

(13) FIG. 1a and FIG. 1b only illustrate the basic arrangement in a force transmission device 1 with a rotational speed adaptive absorber 5 between two dampers 3 and 4 which can be connected in series in a highly simplified schematic depiction, wherein the dampers 3 and 4 are connected in series at least in one force flow direction, in this instant case in both force flow directions, and act as devices for damping vibrations, this means quasi as an elastic clutch, independently from how the particular dampers 3 and 4 are actually configured.

(14) FIG. 1c and FIG. 1d illustrate in a simplified schematic depiction analogously to FIG. 1b another force transmission device configured according to invention, wherein however both dampers 3 and 4 are only connected in series in their function as an elastic clutch in one force flow direction in one power path I or II. According to FIG. 1c, thus the assembly of both dampers 3 and 4 connected in series is always connected subsequent to the mechanical power path II, viewed in the force flow direction between the input E and the output A. The connection of the hydrodynamic component 6, in particular the turbine shell T is performed here between the two dampers 3 and 4. The rotational speed adaptive absorber 5 is thus disposed subsequent to the hydrodynamic component 6 in force flow direction 6 in this case. The rotational speed adaptive absorber 5 is also disposed between the two dampers 3 and 4, wherein the connection is either performed directly at the turbine shell T or at the connection or in the area of the connection of the turbine shell T with the damper 4.

(15) On the other hand, FIG. 1d illustrates and embodiment in which the two dampers 3 and 4 are connected in series always after the hydrodynamic component 6 in the force flow from the input E to the output A, wherein the damper 3 acts as an absorber for a mechanical power transmission, while the damper 4 entirely acts as a vibration damper configured as an elastic clutch. Also here the rotational speed adaptive absorber 5 is either connected directly in front of the damper 4 and thus for a power transmission through the hydrodynamic component 6 at least indirectly connected with the turbine shell T, herein indirectly connected to the damper 3. Furthermore, the rotational speed adaptive absorber 5 is always effective in this embodiment also for a purely mechanical power transmission in the second mechanical power path II, since it is connected together with the damper 4.

(16) FIG. 2 and FIG. 3 illustrate two particularly advantageous embodiments of force transmission devices 1 configured according to the invention in a configuration according the FIG. 1c with reference to a detail from an axial sectional view of the force transmission devices.

(17) FIG. 2 thus illustrates an embodiment with a separate configuration of the rotational speed adaptive absorber 5 and its connection with the damper assembly 2. The rotational speed adaptive absorber 5 is configured as a centrifugal force pendulum device 8 and includes one, preferably several inertial masses 9.1, 9.2 which are supported at an inertial mass support device 10 moveable relative thereto. Thus, the support is performed, for example, through support rollers 11. The inertial mass support device 10 is configured herein as a disc shaped element which forms a hub component 12, which is configured in radial direction with respect to the rotation axis R in the radially inner portion of the disc shaped element or it can also be connected with a hub component 12 of this type. The inertial mass device 10 is preferably configured as a flat planar element or at least as an annular disc shaped element. Also configurations with a cross sectional shaping, for example, in the form of shaped sheet metal components are conceivable. Advantageously, inertial masses 9.1 and 9.2 are provided on both sides of the inertial mass support device 10. These are advantageously supported in the portion of the radially outer diameter of the inertial mass support device 10 through the running track 11, so they perform a pendulum type movement relative to the inertial mass support device. Due to the centrifugal mass influence, the inertial masses 9.1, 9.2 adjust at least in radial direction to the outside, furthermore at least one inertial mass 9.1, 9.2 can move starting at a center position in which the largest distance of its center of gravity S from the center axis M is provided, which corresponds to the rotation axis R of the force transmission device, relative to the hub component 12 along a movement track back and forth into a displaced position, wherein the distance of the center of gravity S of the at least one inertial mass 9.1, 9.2 changes relative to the center position. The inertial mass support device 10 is formed here by a separate element. Thus, the entire centrifugal force pendulum unit 8 can be preassembled separately and can be stored and handled separately as a component.

(18) The force transmission device 1 includes a hydrodynamic component 6, wherein only a detail of the secondary shell functioning as a turbine shell T is illustrated here, wherein the secondary shell is coupled to the output A at least indirectly torque proof. The output A is formed here, for example, by a shaft 29, which is only indicated and which can be formed by a transmission input shaft for use in drive trains for motor vehicles, or can be formed by an element coupled torque proof with the input shaft, in particular a hub 12. The hub 12 is also designated as a damper hub. The coupling of the turbine shell T with the output A is performed here through the damper assembly 2, in particular the second damper 4. The damper assembly 2 includes two dampers 3 and 4, which can be connected in series, respectively forming a damper stage, wherein the two damper stages are disposed offset to one another in radial direction, thus forming a first outer and a second inner damper stage. The dampers 3 and 4 are configured here as single dampers. However, configuring them as series or parallel dampers is also feasible. Thus, advantageously, the first radial damper stage is configured as a radially outer damper stage for implementing the space and installation space saving arrangement. This means it is arranged on a larger diameter than the second radially inner damper stage. The two dampers 3 and 4 or the damper stages formed by them are connected in series in the force flow between the input E and the output A, viewed over the device 7 for circumventing the hydrodynamic component 6 configured as a lockup clutch. The device 7 for bridging configured as a lockup clutch, thus includes a first clutch component 13 and a second clutch component 14, which can be brought into operative engagement with one another at least indirectly torque proof; this means directly or indirectly through additional transmission elements. The coupling is thus performed through friction pairings, which are formed by the first and second clutch components 13 and 14. The first clutch component 13 is thus connected at least indirectly torque proof with the input E, advantageously directly connected therewith, while the second clutch component 14 is coupled at least indirectly torque proof with the damper assembly 2, in particular the first damper 3, preferably directly with the input of the first damper 3. The first and the second clutch components 13 and 14 include an inner disk packet and an outer disk packet in the illustrated case, wherein in the illustrated case, the inner disk packet is made of inner disks supported at an inner disk support, which inner disks form axially aligned surface portions, which can be brought into operative engagement with surface portions complementary thereto, which surface portions are disposed at outer disks disposed at the outer disk support of the first clutch component 13. At least a portion of the inner disks and of the outer disks is thus movably supported in axial direction at the respective disk support. The second clutch component 14 is coupled here with an element disposed in the force flow direction from the input E to the output A, wherein the element functions as an input component for the damper 3. The element is designated as primary component 15. The first damper 3 furthermore comprises a secondary component 16, wherein the primary component 15 or the secondary component 16 are coupled with one another through torque transmission devices 17 and damping coupling devices 18, wherein the means for damping coupling devices 18 are formed by the torque transmission devices 17, and in the simplest case by elastic elements 19, in particular spring units 20. The primary component 15 and the secondary component 16 are thus rotatable relative to one another in circumferential direction. This also applies analogously for the second damper 4, which is configured herein as a radially inner damper and thus as an inner damper. The damper also includes a primary component 21 and a secondary component 22, which are coupled with one another through torque transmission devices 23 and damping coupling devices 24, wherein the primary component 21 and the secondary component 22 are rotatable relative to one another in circumferential direction within limits. Also here, the torque transmission devices 23 can be formed by the damping coupling devices 24, or they can be functionally integrated into a component, preferably in the form of spring units 25. Primary components 15 and secondary components 16 or 21 and 22 of the two dampers 3 and 4 can thus be configured in integrally or in several components. Advantageously, respectively one of the two is made from two disk elements coupled with one another torque proof, between which the respective other component, the secondary component 22, 16 or the primary component 21, 15, is disposed.

(19) In the illustrated embodiment, the respective primary component 15 or 21 functions as an input component for a power transmission between the input E and the output A, while the secondary component 16 or 22 functions as an output component of the respective damper 3, 4. The input component, and thus the primary component 15 of the first damper 3, is formed by a disk shaped element in the form of a drive flange 32. The secondary component 16 is formed by two elements, also designated as drive disks 33, which are disposed in axial direction on both sides of the primary component 15 and coupled torque proof with one another. Thus, the secondary component 16 of the first damper 3 is connected torque proof with the primary component 21 of the second damper 4 or forms an integral unit therewith, wherein also an integral embodiment between the primary component 21 and the secondary component 16 is possible. The primary component 21 of the second damper 4 is formed herein by two disk shaped elements also designated as drive disks 35, while the secondary component 22 is formed by a disk shaped element disposed in axial direction between the drive disks 35, in particular a flange 34; this means it is formed by an intermediary disk, which is connected torque proof with the output A, herein in particular the hub 12. The primary component 12 of the second damper 4 is further connected torque proof with the turbine shell T, in particular the secondary shell of the hydrodynamic component 6. In the simplest case, the coupling 30 is performed through friction locked and/or form locked connections. In the illustrated case, a connection is selected in the form of a rivet joint, wherein the rivets can either be configured as extruded rivets or as separate rivets. Furthermore, the connection between the secondary component 22 and the turbine shell T is used in order to facilitate the coupling 31 with the rotational speed adaptive absorber 5. The rotational speed adaptive absorber, in particular the inertial mass support device 10 configured as a disk shaped element, is disposed and connected in this embodiment in axial direction between the primary component 21 of the second damper 4, which primary component is formed by the drive disks 35, and the turbine shell T or an element coupled torque proof with the turbine shell T. In this embodiment, no particular specification is required for the configuration of the damper assembly 2 based on the separate configuration. Herein, standardized components can be selected, which can be supplemented with the rotational speed adaptive absorber 5. The rotational speed adaptive absorber 5 can thus be pre-assembled and also replaced as a unit that can be handled separately. Furthermore, the rotational speed adaptive absorber or components thereof, in particular the inertial masses 9.1, 9.2, can be disposed using the installation space in radial direction above the second damper 4. The disposition of the absorber 5 is performed here in axial direction, especially between the damper assembly 2 and the hydrodynamic component 6.

(20) On the other hand, FIG. 3 illustrates a particularly advantageous improvement according to FIG. 2, in which the rotational speed adaptive absorber 5 is a component of an element of the damper assembly 2, in particular of the primary component 21 of the second damper 4. In this embodiment, thus at least one drive disk 35 of the primary component 21 and the inertial mass support device 10 form an integral unit, or are formed by a component. Thus, the drive disk 35 is extended in radial direction towards the inner circumference 36, and extends into the portion of the outer circumference 28 of the first damper 3 in radial direction and beyond. In particular for the arrangement of the two dampers 3 and 4 illustrated in FIG. 3 with an offset in axial direction and in radial direction, thus the gained or freely available installation space can be used in an optimum manner.

(21) The configuration of an absorber, which can be adapted to a speed of rotation. can be embodied in many ways. Reference is made in this context to the printed documents DE 10 2006 028 556 A1 and DE 198 31 160 A1. The disclosure of these printed documents with respect to embodiments of rotational speed adaptive tuned mass vibration dampers is thus included into the instant application in its entirety. Absorbers are adaptive to a rotational speed when they can absorb rotational vibrations over a large rotational speed range, ideally over the entire rotational speed range of the drive engine. The inertial masses 9.1, 9.2 thus tend due to gravity to move on a maximum radius relative to the torque induction axis. Through the superposition of the rotational movement with the rotational vibrations, a pendulum type relative movement of the inertial masses 9.1, 9.2 is caused. They adjust with respect to their position solely based on the centrifugal force or based on their weights, this also applies for their resetting. There is no separate resetting force. Furthermore, the resonance frequency is proportional to the rotational speed, so that rotational vibrations with frequencies, which are proportional to the rotational speed n in the same manner, can be absorbed over a large rotational speed range. Thus, the inertial masses 9.1. 9.2 of absorbers 5 move in a purely translatoric manner on a circular movement path relative to the hub component. An embodiment is known for the printed document DE 198 31 160 A1, for which the movement path is characterized e.g. by a curvature radius, which changes at least in sections for an increasing displacement of the inertial masses 9.1, 9.2 from the center position. This applies also for the embodiment of DE 10 2006 028 556 A1. A configuration of this type is depicted in a side view in an exemplary manner as a configuration of a rotational speed adaptive absorber 5 in FIG. 4. This is an exemplary embodiment. Other configurations are conceivable. A configuration of an annular disk shaped element as inertial mass support device 10 is conceivable herein, and the particular inertial masses 9.1-9.n disposed thereon distributed in circumferential direction. In the illustrated case, four inertial masses configured as pendulum masses 9.11-9.14 are movably disposed. These are retained with jacketed shoulder bolts 26 and through support rollers 27 movably at the pendulum mass support device 10.

(22) FIG. 2 and FIG. 3 illustrate particularly advantageous applications in a force transmission device 1, and other configurations are conceivable. FIG. 5 illustrates the direct coupling of the rotational speed adaptive absorber 5 with the turbine shell T of the hydrodynamic component 6. Since the turbine shell T of the hydrodynamic component is connected torque proof with the primary component 21 of the second damper 4, either directly or through additional intermediary elements, also here, an intermediary connection of the absorbers 5 between the two dampers 3 and 4 is provided in the force flow between in the input E and the output A. The disposition at the turbine shell T can thus be performed in the portion of the radial outer circumference 37 of the turbine shell T, thus the disposition can be performed on a radius that is equal to or greater than the radial extension of the turbine shell T or smaller and quasi besides it in axial direction.

(23) Additional connections are described in a schematically simplified illustration in the FIGS. 6a-6d. For the embodiment according to FIG. 6a, the first damper 3 is configured analogously to the embodiments described in FIGS. 2 and 3. The second damper 4 is characterized in that the primary component 21 is formed by the intermediary disk, and the secondary component 22, which is coupled torque proof with the output A, is formed by two side disks 35 disposed in axial direction next to the intermediary disk 34. In this case, the rotational speed adaptive absorber 5 is connected torque proof with the connection between the secondary component 16 of the first damper 3 configured in the form of drive disks 33 and the intermediary disk 34 in the form of the second damper, preferably connected torque proof with the drive disk 33. This holds analogously also for the turbine shell T.

(24) In another embodiment in which the damper assembly 2 includes a first damper 3, in which the primary component 15 is formed, for example, by two drive disks 33, which are at least indirectly coupled with the input E and the secondary component 16 is formed by an intermediary disk in the form of a flange 32. The coupling of the secondary component 16 can either be performed through the primary component 21 configured as a drive disk 35 or by a primary component 21 of the second damper 4 formed by an intermediary disk or a flange 34. According to FIG. 6b, the primary component 21 of the second damper 4 is configured analogously to the embodiments according to FIGS. 2 and 3; this means it is formed by two drive disks 35 or by one drive disk 35. The secondary component 22 is formed by the flange 34. The primary component 15 of the first damper 3 is formed by two drive disks 33 coupled torque proof with one another and the secondary component 16 is formed by a flange 32. The secondary component 16 configured as a flange 32 thus forms an integral unit with the drive disks 35 or one of the drive disks 35 and thus of the primary component 21 of the second damper 4. Thus, it is also conceivable to form these components from separate elements which are coupled torque proof with one another. Also, the drive disks 35 of the first and also the second damper 3, 4 are respectively coupled torque proof with one another, wherein the coupling can be performed in many ways. The turbine shell T of the hydrodynamic component 6 is coupled in this embodiment with the primary component 21, in particular the drive disks 35. With respect to the disposition of the rotational speed adaptive absorber 5, there is a plurality of options also here. The absorber 5 can either be coupled directly with the turbine shell T, the primary component 21 of the second damper 4, in particular one of the drive disks 35, or with the flange 32 of the first damper 3. The particular options for the arrangement are represented here in dash-dotted lines.

(25) Compared to that, FIG. 6c illustrates a configuration of the first damper 3 according to FIG. 6b. However, herein the primary component 21 of the second damper 4 is formed by the flange 34. The secondary component 22 is formed by the drive disks 35. The connection of the turbine shell T is performed in this case at the flange 34. The rotational speed adaptive absorber 5 is then either coupled directly with the turbine shell T or the flange 34, which simultaneously forms the flange 32 of the first damper 3.

(26) Thus, in FIG. 6c the second damper 4 acts in the hydrodynamic power path 1 as an elastic clutch, the first damper 3 acts as a absorber. This applies analogously also for the embodiment according to FIG. 6a and FIG. 6b.

(27) FIG. 6a and FIG. 6b illustrate embodiments in which the two dampers are disposed in axial direction viewed from the input E to the output A of the force transmission device 1 offset relative to one another, and FIG. 6c illustrates an embodiment with a disposition of the two damper stages in one axial plane.

(28) FIGS. 6a-6c furthermore illustrate embodiments with an effect of the damper 3 for a hydrodynamic power transmission as an absorber. Contrary thereto, FIG. 6d illustrates an embodiment with a function of both dampers 3, 4 in both power paths as an elastic coupling. For this elastic coupling, the primary components 15 and 21 of the two dampers 3 and 4 and the secondary component 16 and 22 of the dampers 3 and 4 are formed respectively by like components. The series connection is implemented by the free angle in the dampers in circumferential direction. For example, the openings of the outer damper 3, which support the force transmission devices, and which form stops in circumferential direction, are provided with a free angle portion in unloaded condition, while the openings at the inner damper 4 are configured so that the torque transmission devices, in particular the spring elements 35, are always in contact. In the illustrated case, for example, the primary components 15 and 21 are formed by two drive disks 33 or 35, the secondary components 16, 22 are formed by a flange 34 or 32 disposed between the secondary components, wherein the flange is coupled torque proof with the output A. The connection of the device 7 and also of the turbine shell T is thus performed at one of the drive disks 33, 35, wherein the damper assembly 2 viewed in axial direction in three dimensions is disposed between the device 7 and the hydrodynamic component 6. The connection of the rotational speed adaptive absorber 5 is performed here at one of the drive disks 33, 35, advantageously at the drive disk at the side of the turbine shell.

(29) The spatial arrangement between the input E and the output A is performed for almost all embodiments according to FIGS. 6a-6c as a function of the arrangements of the particular dampers 3, 4 with an offset in axial- and in radial direction. When the offset is provided, then the intermediary space in radial direction can be used in an optimum manner for the arrangement of the rotational speed adaptive absorber 5. Otherwise, the arrangement is performed in axial direction adjacent to the particular dampers.

(30) For the damper assemblies 2 illustrated in FIGS. 1-6, the particular dampers 3 and 4 are formed by so-called single dampers provided as mechanical dampers, wherein the single dampers are configured as compression spring dampers or arc spring dampers. This means that the torque transmission devices 17, 13 and the damping coupling devices 18, 24 are formed by the spring units 20, 25 configured as arc springs or compression springs. However, also other damper concepts are conceivable, for example, combined mechanical-hydraulic dampers.

(31) It is furthermore also conceivable to use the solution according to the invention in multiple damper assemblies, in which the particular dampers 3 and 4 already form a damper stage by themselves and are configured as multiple dampers in the form of parallel- or series dampers.

(32) FIG. 7 illustrates the rotational speed variations in a drive train with respect to a diagram, in which the rotational speed variation in the drive train is plotted over the engine speed n, comparing an embodiment of a force transmission device without a rotational speed adaptive absorber 5 with a dashed line and a force transmission device 1 with a rotational speed adaptive absorber 5 with a solid line. This indicates that the rotational speed variations are much greater for a conventional solution, while much lower rotational speed variations occur for a power transmission in an embodiment according to FIG. 3, in particular in critical rotational speed ranges.

REFERENCE NUMERALS AND DESIGNATIONS

(33) 1 force transmission device 2 damper assembly 3 damper 4 damper 5 rotational speed adaptive absorber 6 hydrodynamic component 7 lock up device for bridging hydrodynamic component 8 centrifugal force pendulum 9 centrifugal mass 9.1, 9.2, 9.11 9.12, 9.13, 9.14 inertial mass 10 inertial mass support device 11 support rollers 12 hub component 13 first clutch component 14 second clutch component 15 primary component 16 secondary component 17 torque transmission device 18 damping coupling device 19 elastic element 20 spring unit 21 primary component 22 secondary component 23 torque transmission device 24 damping coupling device 25 spring device 26 shoulder bolt 27 support roller 28 outer circumference 29 shaft 30 coupling 31 coupling 32 drive flange 33 drive discs 34 drive flange 35 drive discs 36 inner circumference 37 outer circumference 100 drive engine 101 output E input A output P pump shell T turbine shell AR operating cavity L stator shell I first power path II second power path R rotation axis S center of gravity M center axis N engine speed