Force transmission device with a rotational speed adaptive damper and method for improving the damping properties

Abstract

The invention relates to a force transmission device for power transmission between an input and an output, comprising at least an input and an output, and a vibration damping device disposed in a cavity that can be filled at least partially with an operating medium, in particular oil, the vibration damping device coupled with a rotational speed adaptive absorber, wherein the rotational speed adaptive absorber is tuned as a function of an oil influence to an effective order q_eff, which is greater by an order shift value q_F than an order q of an exciting vibration of a drive system.

Description

RELATED APPLICATIONS

This patent application tuned mass temper

Path radius of rollers:

$R_{\mathrm{eff}}=\frac{l_{\mathrm{eff}}}{2}-r$

In order to achieve the desired insulation of the rotational speed adaptive absorber in oil, for example, in a hydrodynamic component, the absorber has to be configured for a higher order, this means the shift of the absorption order through the oil, in particular through the oil pressure and the forces resulting there from have to be considered for the configuration as well. Since the shift of the absorption order through the oil can be expressed as a movement of the center of gravity of the inertial masses or pendulum masses, the shift through the oil can be substantially compensated by changing the geometry of the inertial masses and the geometry of their centers of gravity.

The method according to the invention can be implemented as described infra: Initially, the order of the excitation is determined in a first step. It is essential that a shift to a higher order is selected as a function of the order of the excitation as a starting point, wherein the shift is in a range of 0.05-0.5, wherein the configuration is based on the respective ideal conditions of a dry centrifugal force pendulum during an operating mode with the system operative. Thus an order shift is predetermined which is disposed in a range of 0.05-0.5. As a function of the order shift the connection and thus the center of gravity path is determined considering the oil influence, while the geometry of the inertial masses 9.11-9.14 is known. This yields the effective center of gravity distance S_eff, where the center of gravity is subsequently linked. This yields the additional required geometric variables, like the effective radius of the center of gravity path, effective radius of the center of the center of gravity path and the path radius of the support rollers. The center of gravity path can thus be configured, so that it differs from a circular path.

Reference Numerals and Designations

1 force transmission device

2 damper assembly

3 damper

4 damper

5 rotational speed adaptive absorber

6 hydrodynamic component

7 lock up device for hydrodynamic component

8 centrifugal force pendulum

9 inertial 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 drive flange

32 drive discs

33 drive flange discs

34 drive discs

35 inner circumference drive disc

36 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

S center of gravity distance as a function of the order q of the exciting vibration of the drive

M mass

S_eff effective center of gravity distance

p oil density

r effective radius of inertial mass

I_eff effective radius of the center of gravity path

L_eff effective radius of the center of the center gravity path

Claims

2. The force transmission device according to claim 1, wherein the order shift value q_F is selected, so that a resonance of the rotational speed adaptive absorber does not coincide with the order q of the exciting vibration.

3. The force transmission device according to claim 1, wherein the effective order q_eff of the rotational speed adaptive absorber exceeds the order q of the exciting vibration of the drive by the order shift value q_F in the range of >0.05 to 0.5.

4. The force transmission device according to claim 1, wherein the rotational speed adaptive absorber is configured as a centrifugal force pendulum device, comprising an inertial mass support device with inertial masses disposed thereon and movable relative thereto, configured and designed, so that a center of gravity distance S of a particular inertial mass is determined as a function of an order q of the exciting vibration of the drive and the order shift by q_f to an effective order q_eff defines a change of the center of gravity distance as a function of the order shift value q_f.

5. The force transmission device according to claim 1, wherein a size of the order shift value q_f changes proportional to a change of the order q of the excitation of the drive.

6. The force transmission device according to claim 1, comprising a hydrodynamic component with at least a primary shell functioning as a pump shell (P) and a secondary shell functioning as turbine shell (T) jointly forming an operating space (AR), wherein the turbine shell (T) is connected at least indirectly torque proof with the output (A) of the force transmission device and a device for bridging the hydrodynamic components, which are respectively disposed in a power path, and the device for damping vibrations is connected with the rotational speed adaptive absorber at least in series with one of the power paths, wherein a cavity which can be at least partially filled with an operating medium, is formed by an inner cavity of the force transmission device which inner cavity is flowed through by the operating medium of the hydrodynamic component.

7. The device of claim 1, wherein the operating medium is oil.

8. The force transmission device according to claim 1, wherein the effective order q_effof the rotational speed adaptive absorber exceeds the order q of the exciting vibration of the drive by the order shift value q_F in the range of >0.05 to 0.4.

9. The force transmission device according to claim 1, wherein the effective order q_eff of the rotational speed adaptive absorber exceeds the order q of the exciting vibration of the drive by the order shift value q_F in the range of >0.05 to 0.3.

10. The force transmission device according to claim 1, wherein the effective order q_eff of the rotational speed adaptive absorber exceeds the order q of the exciting vibration of the drive by the order shift value q_F in the range of >0.14 to 0.3.

12. The method for improving the damping properties of a force transmission device according the claim 11, comprising the following method steps:

determining the order of excitation q of a drive engine;

defining a geometry of the rotational speed adaptive absorber for the order of excitation q;

determining the required order shift value q_F; and

determining the geometry of the absorber as a function of the order shift value q_F.

13. The method of claim 11, wherein the operating medium is oil.

11. A method for improving the damping properties of a force transmission device for power transmission between an input and an output, comprising at least an input (E) and an output (A), and a vibration damping device disposed in a cavity that can be filled at least partially with an operating medium, the cavity in particular flowed through by an operating medium of a hydrodynamic component, the vibration damping device coupled with a rotational speed adaptive absorber, wherein the rotational speed adaptive absorber is tuned as a function of an oil influence to an effective order q_eff, which is greater by an order shift value q_F than an order q of an exciting vibration of a drive system.

1. A force transmission device for power transmission between an input and an output, comprising:

at least an input (E) and an output (A); and

a vibration damping device disposed in a cavity that can be filled at least partially with an operating medium, the vibration damping device coupled with a rotational speed adaptive absorber,

wherein the rotational speed adaptive absorber is tuned as a function of an oil influence to an effective order q_eff, which is greater by an order shift value q_F than an order q of an exciting vibration of a drive system.

14. A force transmission device, comprised of a torque converter, for power transmission between an input and an output, comprising:

at least an input (E) and an output (A);

a lock-up clutch; and

a vibration damping device disposed in a cavity that can be filled at least partially with an operating medium, the vibration damping device coupled with a rotational speed adaptive absorber in the form of a centrifugal force pendulum, the rotational speed adaptive absorber being positioned after the vibration damping device in the force flow direction,

wherein the rotational speed adaptive absorber is tuned as a function of an oil influence to an effective order q_eff, which is greater by an order shift value q_F than an order q of an exciting vibration of a drive system,

wherein the operating medium is oil and the oil influence is that of rotating oil in the cavity, which is flowed through with oil, on an inertial mass of the rotational speed adaptive absorber, wherein the effective order q_eff of the rotational speed adaptive absorber exceeds the order q of the exciting vibration of the drive system by the order shift value q_F in the range of >0.05 to 0.5, and

wherein the order shift value q_F is approximately 0.14, and the order q of the exciting vibration is 2.0.

15. A method for improving the damping properties of a force transmission device, comprised of a torque converter, for power transmission between an input and an output, comprising at least an input (E) and an output (A),

a lock-up clutch;

and a vibration damping device disposed in a cavity that can be filled at least

partially with an operating medium, the cavity in particular flowed through by an operating medium of a hydrodynamic component, the vibration damping device coupled with a rotational speed adaptive absorber, in the form of a centrifugal force pendulum,

wherein the method includes tuning the rotational speed adaptive absorber as a function of an oil influence to an effective order q_eff, which is greater by an order shift value q_F than an order q of an exciting vibration of a drive system,

wherein the rotational speed adaptive absorber is positioned after the vibration damping device in the force flow direction, wherein the operating medium is oil and the oil influence is that of rotating oil in the cavity on an inertial mass of the rotational speed adaptive absorber, wherein the method includes making the effective order q_eff of the rotational speed adaptive absorber exceed the order q of the exciting vibration of the drive system by the order shift value q_F in the range of >0.05 to 0.5,

and wherein the order shift value q_F is approximately 0.14, and the order q of the exciting vibration is 2.0.

16. A force transmission device, comprised of a torque converter, for power transmission between an input and an output, comprising:

at least an input (E) and an output (A);

a lock-up clutch;

a vibration damping device disposed in a cavity that can be filled at least partially with an operating medium, in the form of oil, that rotates during operation of the torque converter; and

a centrifugal force pendulum absorber coupled with the vibration damping device, the centrifugal force pendulum absorber (i) being positioned in the cavity and after the vibration damping device in the force flow direction, and (ii) comprising an inertial mass support device with at least one inertial mass disposed thereon and moveable relative thereto,

wherein the centrifugal force pendulum absorber is tuned as a function of an influence of the rotating oil to an effective order q_eff, which is greater by an order shift value q_F than an order q of an exciting vibration of a drive system,

wherein the influence is caused by relative movement between the at least one inertial mass and the rotating oil, which rotating oil is flowed through the cavity during operation of the torque converter, and which influence on the at least one inertial mass causes a shifting of an order of the centrifugal force pendulum absorber to a lower order, and

wherein the order shift value q_F is approximately 0.14, and the order q of the exciting vibration is 2.0.

17. The force transmission device according to claim 16, wherein the inertial mass support device is configured so that a center of gravity distance S of a particular inertial mass is determined as a function of the order q of the exciting vibration of the drive system and the order shift by q_F to the effective order q_eff defines a change of the center of gravity distance as a function of the order shift value q_F.

18. The force transmission device according to claim 16, comprising a hydrodynamic component with at least a primary shell functioning as a pump shell (P) and a secondary shell functioning as a turbine shell (T) jointly forming an operating space (AR), wherein the turbine shell (T) is connected at least indirectly torque proof with the output (A) of the force transmission device and a device for bridging the hydrodynamic components, which are respectively disposed in a power path, and the vibration damping device is connected with the centrifugal force pendulum absorber at least in series with one of the power paths, wherein the cavity is formed by an inner cavity of the force transmission device, in which the inner cavity is flowed through by the oil of the hydrodynamic component during operation.

19. The force transmission device according to claim 18, wherein a movement path of a particular inertial mass relative to the inertial mass support device has a radius of curvature that changes with increasing displacement of the particular inertial mass.

20. A force transmission device, comprised of a torque converter, for power transmission between an input and an output, comprising:

at least an input (E) and an output (A);

a lock-up clutch;

a vibration damping device disposed in a cavity that can be filled at least partially with an operating medium, in the form of oil, that rotates during operation of the torque converter; and

a centrifugal force pendulum absorber coupled with the vibration damping device, the centrifugal force pendulum absorber (i) being positioned in the cavity and after the vibration damping device in the force flow direction, and (ii) comprising an inertial mass support device with at least one inertial mass disposed thereon and moveable relative thereto,

wherein the centrifugal force pendulum absorber is tuned as a function of an influence of the rotating oil to an effective order q_eff, which is greater by an order shift value q_F than an order q of an exciting vibration of a drive system,

wherein the influence is caused by relative movement between the at least one inertial mass and the rotating oil, which rotating oil is flowed through the cavity during operation of the torque converter, and which influence on the at least one inertial mass causes a shifting of an order of the centrifugal force pendulum absorber to a lower order, and

wherein the order shift value q_F is approximately 0.21, and the order q of the exciting vibration is 3.0.

21. The force transmission device according to claim 20, wherein the inertial mass support device is configured so that a center of gravity distance S of a particular inertial mass is determined as a function of the order q of the exciting vibration of the drive system and the order shift by q_F to the effective order q_eff defines a change of the center of gravity distance as a function of the order shift value q_F.

22. The force transmission device according to claim 20, comprising a hydrodynamic component with at least a primary shell functioning as a pump shell (P) and a secondary shell functioning as a turbine shell (T) jointly forming an operating space (AR), wherein the turbine shell (T) is connected at least indirectly torque proof with the output (A) of the force transmission device and a device for bridging the hydrodynamic components, which are respectively disposed in a power path, and the vibration damping device is connected with the centrifugal force pendulum absorber at least in series with one of the power paths, wherein the cavity is formed by an inner cavity of the force transmission device, in which the inner cavity is flowed through by the oil of the hydrodynamic component during operation.

23. The force transmission device according to claim 22, wherein a movement path of a particular inertial mass relative to the inertial mass support device has a radius of curvature that changes with increasing displacement of the particular inertial mass.

24. A force transmission device, comprised of a torque converter, for power transmission between an input and an output, comprising:

at least an input (E) and an output (A);

a lock-up clutch; and

a vibration damping device disposed in a cavity that can be filled at least partially with an operating medium, the vibration damping device coupled with a rotational speed adaptive absorber in the form of a centrifugal force pendulum, the rotational speed adaptive absorber being positioned after the vibration damping device in the force flow direction,

wherein the rotational speed adaptive absorber is tuned as a function of an oil influence to an effective order q_eff, which is greater by an order shift value q_F than an order q of an exciting vibration of a drive system,

wherein the operating medium is oil and the oil influence is that of rotating oil in the cavity, which is flowed through with oil, on an inertial mass of the rotational speed adaptive absorber, and

wherein the effective order q_eff of the rotational speed adaptive absorber exceeds the order q of the exciting vibration of the drive system by the order shift value q_F by approximately 7%.

25. The force transmission device according to claim 24, wherein the inertial mass support device is configured so that a center of gravity distance S of a particular inertial mass is determined as a function of the order q of the exciting vibration of the drive system and the order shift by q_F to the effective order q_eff defines a change of the center of gravity distance as a function of the order shift value q_F.

26. The force transmission device according to claim 24, comprising a hydrodynamic component with at least a primary shell functioning as a pump shell (P) and a secondary shell functioning as a turbine shell (T) jointly forming an operating space (AR), wherein the turbine shell (T) is connected at least indirectly torque proof with the output (A) of the force transmission device and a device for bridging the hydrodynamic components, which are respectively disposed in a power path, and the vibration damping device is connected with the centrifugal force pendulum absorber at least in series with one of the power paths, wherein the cavity is formed by an inner cavity of the force transmission device, in which the inner cavity is flowed through by the oil of the hydrodynamic component during operation.

27. The force transmission device according to claim 26, wherein a movement path of the inertial mass relative to the inertial mass support device has a radius of curvature that changes with increasing displacement of the inertial mass.