DAMPING DEVICE FOR A POWERTRAIN OF A MOTOR VEHICLE, IN PARTICULAR A CAR, AND POWERTRAIN COMPRISING SUCH A DAMPING DEVICE

Abstract

A damping apparatus for a drivetrain of a motor vehicle, with a first damping element which is rotatable about an axis of rotation, a second damping element which can be driven by the first damping element and is thereby rotatable about the axis of rotation, at least two damping chambers, the volumes of which can be modified by a relative rotation between the damping elements, at least one overflow channel, by which the damping chambers are connected to one another fluidly, and having a damping fluid, which flows from one damping chamber into the other damping chamber via the overflow channel upon a volume reduction of one of the damping chambers. The overflow channel flowing into the respective damping chambers at both ends is formed by a gap between the damping elements, the gap being directly limited by the damping elements, at least in a lengthwise region.

Claims

1-14. (canceled)

15. A damping apparatus for a drivetrain of a motor vehicle, comprising: a first damping element which is rotatable about an axis of rotation; a second damping element which can be driven by the first damping element and is thereby rotatable about the axis of rotation; at least two damping chambers, the volumes of which can be modified by a relative rotation between the damping elements; at least one overflow channel, by means of which the damping chambers are connected to one another fluidly; and a damping fluid, which flows from one damping chamber into the other damping chamber via the overflow channel upon a volume reduction of one of the damping chambers, wherein the overflow channel flowing into the respective damping chambers at both ends is formed by a gap between the damping elements, said gap being directly limited by the damping elements, at least in a lengthwise region.

16. The damping apparatus according to claim 15, wherein the overflow channel is formed, at least predominantly, particularly completely, by the gap.

17. The damping apparatus according to claim 15, wherein the width of the gap can be adjusted in order to adjust the damping effect of the damping apparatus.

18. The damping apparatus according to claim 17, wherein at least one adjusting element is provided, which is moveable relative to at least one of the damping elements and directly limits at least one portion of the gap, it being possible to adjust the width of the gap by means of said adjusting element.

19. The damping apparatus according to claim 18, wherein the adjusting element is a component of one of the damping elements.

20. The damping apparatus according to claim 19, wherein the adjusting element is retained in a movable manner on a corresponding structural element of the one damping element, a component of which is the adjusting element.

21. The damping apparatus according to claim 17, wherein the width of the gap can be adjusted by means of at least one thread.

22. The damping apparatus according to claim 20, wherein the adjusting element has the thread and is retained in a movable manner on the structural element via the thread and via a corresponding further thread provided on the structural element.

23. The damping apparatus according to claim 15, wherein the damping elements directly limit the damping chambers.

24. The damping apparatus according to claim 15, wherein at least one wall region limiting at least one of the damping chambers has a bow-shaped profile.

25. The damping apparatus according to claim 24, wherein the bow-shaped profile extends over the entire radial extension of the at least one damping chamber.

26. A damping apparatus for a drivetrain of a motor vehicle, comprising: a first damping element, which is rotatable about an axis of rotation; and a second damping element, which can be driven by the first damping element and is thereby rotatable about the axis of rotation, wherein the damping elements have respective threads screwed together, by means of which a relative rotation between the damping elements can be converted into a translational relative motion between the damping elements, and at least one damping part, formed from an elastically deformable material, is arranged on at least one of the damping elements, it being possible to move the other respective damping element in supportive contact due to the translational relative motion.

27. The damping apparatus according to claim 26, wherein at least one further damping part, formed from an elastically deformable material and opposite damping part, is arranged on at least one of the damping elements, it being possible to move the other respective damping element in supportive contact due to the translational relative motion.

Description

[0033] FIG. 1 sectionally shows a schematic cross-sectional view of a damping apparatus according to a first embodiment for a drivetrain of a motor vehicle, having at least two damping elements, which are rotatable relative to one another, and having at least one overflow channel, which is formed, at least in a lengthwise region, by a gap between the damping elements directly limited by the damping elements;

[0034] FIG. 2 sectionally shows a schematic and partially sectional side view of the damping apparatus according to FIG. 1 in an exploded view;

[0035] FIG. 3 sectionally shows a schematic cross-sectional view of the damping apparatus according to a second embodiment;

[0036] FIG. 4 sectionally shows a schematic cross-sectional view of the damping apparatus according to a third embodiment; and

[0037] FIG. 5 sectionally shows a schematic and partially sectional side view of the damping apparatus according to a fourth embodiment.

[0038] Similar or functionally equivalent elements have the same reference numbers in the figures.

[0039] FIG. 1 sectionally shows, in a schematic cross-sectional view, a first embodiment of a damping apparatus, characterized as a whole with 10, for a drivetrain of a vehicle, particularly a motor vehicle such as, for example, a passenger car. The damping apparatus 10 according to the first embodiment is shown in a schematic and partially sectional side view in FIG. 2. In the completely manufactured state, the motor vehicle comprises the aforementioned drivetrain, by means of which the motor vehicle can be driven. To this end, the drivetrain comprises, for example, at least one drive motor, which may be formed as an internal combustion engine or electric motor. The drive motor has at least one output shaft formed, for example, as a crankshaft, by means of which the drive motor can provide torques for driving the motor vehicle.

[0040] The drivetrain further comprises a universal shaft formed as a cardan shaft, by means of which, for example, the torques provided by the drive motor can be transferred to at least one axle of the drivetrain. Thus, the cardan shaft can be driven, for example, by the output shaft or by the torques provided by the drive motor via the output shaft. In relation to a torque flow from the drive motor to the axle, at least one further drive element is provided, for example, after or downstream of the cardan shaft, with it being possible to transfer the torques from the cardan shaft to said drive element, so that, for example, the drive element can be driven by the cardan shaft. The cardan shaft is, for example, a shaft of the drivetrain. The damping apparatus 10 is arranged, for example, before or after the cardan shaft such that the damping apparatus 10 is arranged between the output shaft and the cardan shaft or between the cardan shaft and the drive element, for example in relation to the torque flow. Thus, the cardan shaft can be driven, for example, by the output shaft via the damping apparatus 10, or the drive element can be driven by the cardan shaft via the damping apparatus 10. Thus, the aforementioned torques between the cardan shaft and the output shaft or between the cardan shaft and the drive element can be transferred via the damping apparatus 10. The drive element, for example, is a further shaft or a further shaft element of the drivetrain.

[0041] As is shown especially well in FIG. 2, the damping apparatus 10 comprises a first damping element 14, which is rotatable about an axis of rotation 12, and a second damping element 16, which is rotatable about the axis of rotation 12, which can be driven by the first damping element 14 and is thereby rotatable about the axis of rotation 12. In particular, damping elements 14 and 16 are arranged coaxially with respect to one another, particularly in relation to the axis of rotation 12. For example, the aforementioned torques can be transferred to damping element 16 via damping element 14.

[0042] When viewed together with FIG. 1, it can be seen that the damping apparatus 10 has a plurality of damping chambers 18a-d, wherein damping chambers 18a, b, for example, form a first pair of chambers and damping chambers 18c, d form a second pair of chambers. In doing so, the respective damping chamber 18a-d, the respective volume of which can be modified by a relative rotation between damping elements 14 and 16, is arranged between respective damping elements 14 and 16 in the circumferential direction of the damping apparatus 10. In this case, the circumferential direction in FIG. 1 is indicated by a double arrow 20, wherein the circumferential direction extends about the axis of rotation 12. For example, if damping element 14 is rotated relative to damping element 16 in a first direction of rotation 12, indicated by arrow 22 in FIG. 1, this results in a volume reduction of damping chambers 18a, d and a volume increase in damping chambers 18b, c. In doing so, the respective volumes of damping chambers 18a, d are reduced by the same amount that the respective volumes of damping chambers 18b, c are increased.

[0043] For example, if damping element 14 is rotated relative to damping element 16 in a second direction of rotation 12, indicated by arrow 24 in FIG. 1, opposite the first direction of rotation, this results in a respective volume reduction of damping chambers 18b, c and in a respective volume increase in damping chambers 18a, d. In doing so, the respective volumes of damping chambers 18b, c are reduced by the same amount that the respective volumes of damping chambers 18a, d are increased.

[0044] FIG. 1 shows that damping chambers 18a-d are limited, particularly directly, by respective wall regions 26 and 28 of the damping apparatus 10, particularly in the circumferential direction of the damping apparatus 10. In doing so, wall regions 26 are formed by damping element 16, while wall regions 28 are formed by damping element 14. In the radial direction of the damping apparatus 10 outward, the damping chambers 18a-d are limited, for example, by a wall 30, which is formed, for example, by damping element 16, as particularly shown in FIG. 2. For example, at least one overflow channel, by means of which damping chambers 18a, b or 18c, d, particularly of the respective pair of chambers, are fluidly connected to one another, is provided per wall region 28 or per pair of chambers, respectively.

[0045] In addition, the damping apparatus 10 has a damping fluid 32, especially schematically shown in FIG. 1, which may be formed, for example, as a gas or as a fluid, particularly as a viscous fluid. For example, the damping fluid is formed as air. Furthermore, it is conceivable that the damping fluid is formed as hydraulic fluid such as, for example, a viscous oil.

[0046] For example, with such a relative rotation between damping elements 14 and 16, in which a volume reduction of damping elements 18a, d results, the damping fluid initially being held, for example, in damping chambers 18a, d can flow from respective damping chambers 18a, d into respective damping chambers 18b, c via the overflow channels. For example, because the respective overflow channel has a flow diameter that the damping fluid can flow through, which is substantially smaller than respective damping chambers 18a-d, the respective overflow channel, for example, functions as a throttle for the damping fluid such that the relative rotation between damping elements 14 and 16 is damped by means of the damping fluid.

[0047] The contact or edge changes can thereby be damped. If this accordingly results in such a relative rotation between damping elements 14 and 16, in which a volume reduction of damping elements 18b, c results, the damping fluid initially being held in damping chambers 18b, c flows from damping chambers 18b, c into respective damping chambers 18a, d via the overflow channels. In other words, due to a volume reduction in respective damping chamber 18a, d, at least a portion of the damping fluid being held initially in respective damping chamber 18a-d is displaced from respective damping chamber 18a, d such that the displaced portion flows from respective damping chamber 18a, d into the other respective damping chamber 18a-d of the respective pair of chambers, via the respective overflow channel. An excessively hard contact change can thereby be prevented such that the development of undesirable noises can be avoided.

[0048] In order to then implement an especially advantageous damping of the contact or edge changes in an especially simple and economical manner, the respective overflow channel flowing into respective damping chambers 18a, b or 18c, d, respectively, of the respective pair of chambers, at both ends is formed by a gap S between damping elements 14 and 16, said gap being directly limited by damping elements 14 and 16, at least in a lengthwise region, particularly at least predominately or completely. FIG. 1 shows that, with the first embodiment, the respective gap S is limited outward in the radial direction directly by wall region 30 and thus directly by damping element 16, wherein the respective gap S is limited inward in the radial direction directly by respective wall region 28 and thus by damping element 14. The direct limiting is understood to mean that the damping fluid flowing through the respective gap S, particularly in the circumferential direction of the damping apparatus 10, makes direct contact with respective wall region 28 or 30, respectively. Due to this damping of contact or edge changes, load changes, for example, can be damped such that an especially advantageous load change damping can be represented with the drivetrain.

[0049] In order to prevent leakages, for example, as well as undesirable flows of the damping fluid, sealing elements 34, for example, are provided, which are supported, for example, outward in the radial direction on damping element 16, particularly on wall region 30, and supported inward in the radial direction on damping element 14. Damping elements 14 and 16 are sealed off to one another by means of the sealing elements 34. For example, respective sealing element 34 is formed as a seal ring. In addition, at least one securing element is provided, which is formed as a circlip 36 with the first embodiment. By means of the circlip 36, damping elements 14 and 16 are secured relative to one another, for example, in the axial direction and thus along the axis of rotation 12 such that, for example, axial relative motions between damping elements 14 and 16 can be at least limited or prevented by means of the circlip 36.

[0050] In addition, damping element 14 has securing elements 38, by means of which, for example, damping element 14 can be coupled, particularly can be connected in a torsionally resistant manner, with the output shaft or with the cardan shaft. Moreover, damping element 16 has securing elements 40, by means of which damping element 16, for example, can be coupled, particularly can be connected in a torsionally resistant manner, with the cardan shaft or with the aforementioned drive element.

[0051] The gaps S, for example, have different geometries, particularly different widths. In other words, the gaps S, for example, differ from one another in their respective widths extending particularly in the radial direction of the damping apparatus 10, wherein the respective width of the respective gap is also characterized as the gap width.

[0052] For example, in order to adjust the damping effect of the damping apparatus 10 on a need basis, the respective gap S, for example, can be adjusted in its width particularly extending in the radial direction of the damping apparatus 10, wherein the width of the respective gap S is also characterized as the gap width.

[0053] To this end, at least one adjusting element 42, for example, which is moveable relative to at least one of damping elements 14 and 16, particularly in the radial direction of the damping apparatus 10, and directly limits at least one portion of the respective gap S, is provided, particularly per each gap S, it being possible to adjust the respective width of the respective gap S by means of said adjusting element. The respective adjusting element 42 is retained, for example, in a moveable manner on damping element 16, particularly on a corresponding structural element of damping element 16, and can be moved relative to damping element 14 and relative to damping element 16 or the structural element of damping element 16, particularly in the radial direction of the damping apparatus 10.

[0054] In particular due to the radial motion of the adjusting element 42 relative to damping element 14 and the corresponding structural element or damping element 16, the respective width of the respective gap S can be adjusted on a need basis. To this end, the adjusting element 42, for example, has a first thread in the form of an outer thread, wherein damping element 16, for example, or the structural element has a second thread, in the form of an inner thread, corresponding to the first thread. Via the thread, the respective adjusting element 42 is threaded with damping element 16 or with the corresponding structural element of damping element 16 such that the threads interlock. For example, if the adjusting element 42 is rotated about a further axis of rotation, extending, for example, at an angle or perpendicular to the axis of rotation 12, relative to damping element 14 and relative to the corresponding structural element of damping element 16, this relative rotation is converted, by means of the thread, into a translational motion of the adjusting element 42 relative to damping element 14 and the structural element, particularly along the further axis of rotation.

[0055] For example, if the respective adjusting element 42 is rotated such that the respective adjusting element 42 is moved inward in the radial direction, the respective width of the respective gap S, for example, is thereby reduced. In contrast, if the respective adjusting element 42, for example, is moved relative to damping element 14 and the corresponding structural element or damping element 16 such that the respective adjusting element 42 is also moved outward in the radial direction relative to damping elements 14 and 16, the respective width of the respective gap S, for example, is thereby increased. Thus, the respective width of the respective gap S can be adjusted by means of the aforementioned thread such that the respective width and thus the damping effect can be adjusted especially simply and precisely as well as on a need basis.

[0056] With the first embodiment, wall regions 26 and 28 have at least substantially straight or linear contours, by means of which damping chambers 18a-d are limited, particularly in the circumferential direction of the damping apparatus 10. In doing so, the contours of wall regions 26 extend inward toward one another in the radial direction of the damping apparatus 10, wherein the contours of wall regions 28 also extend inward toward one another in the radial direction of the damping apparatus 10.

[0057] FIG. 3 shows a second embodiment of the damping apparatus 10. With the second embodiment, precisely two damping chambers 18a, b are provided, wherein the contours of wall region 26, which directly limit damping chambers 18a, b, extend parallel to one another or coincide. In contrast, the contours of wall region 28, which directly limit damping chambers 18a, b, extend at an angle or perpendicular to one another and, in doing so, extend inward toward one another in the radial direction. The contours are also linear with the second embodiment.

[0058] In contrast to this, in a third embodiment shown in FIG. 4, it is provided that wall regions 26 and 28 directly limiting respective damping chambers 18a-d or the contours thereof directly limiting damping chambers 18a-d have a bow-shaped profile, which extends over the complete radial extension of respective damping chambers 18a-d.

[0059] Finally, FIG. 5 shows a fourth embodiment of the damping apparatus 10. With the fourth embodiment, damping element 14 has a first thread in the form of an inner thread 44, wherein damping element 16 has a second thread in the form of an outer thread 46. In this case, the threads (inner thread 44 and outer thread 46) are screwed together such that the threads interlock. In other words, damping elements 14 and 16 are screwed together via the inner thread 44 and the outer thread 46. The rotating capacity of damping elements 14 and 16 relative to one another about the axis of rotation 12 is indicated by a double arrow 48 in FIG. 5. By means of the threads, relative rotations between damping elements 14 and 16 are converted into a translational relative motion between damping elements 14 and 16.

[0060] In other words, if damping elements 14 and 16 are rotated about the axis of rotation 12 relative to one another, this results in translational relative motions of damping elements 14 and 16, in particular along the axis of rotation 12, wherein said translational relative motions between damping elements 14 and 16 are indicated by a double arrow 50 in FIG. 5. For example, if damping element 16 is rotated, in a first direction of rotation, about the axis of rotation 12 relative to damping element 14, damping element 16, for example, is moved translationally toward damping element 14, along the axis of rotation 12. In contrast, if damping element 16 is rotated, in a second direction of rotation opposite the first direction of rotation, about the axis of rotation 12 relative to damping element 14, damping element 16, for example, is thereby moved away from damping element 14, along the axis of rotation 12. If damping element 16 is moved toward damping element 14, damping element 16 is thus moved relative to damping element 14 in a first direction, along the axis of rotation 12. If damping element 16 is moved away from damping element 14, damping element 16 is moved translationally in a second direction opposite the first direction, relative to damping element 14, along the axis of rotation 12.

[0061] The damping apparatus 10 according to the fourth embodiment comprises a first damping part 52 retained on damping element 14, with said damping part being formed from an elastically deformable material, particularly from rubber or from an elastomer. In this case, the damping part 52 is arranged on a first end wall 54 of damping element 14, with said end wall facing damping element 16. Furthermore, a second damping part 56, opposite damping part 52, is provided on damping element 14, with the second damping part being arranged, for example, on end wall 58, opposite end wall 54, of damping element 14. In doing so, damping parts 52 and 56 or end walls 54 and 58 are positioned opposite one another along the axis of rotation 12, along which damping elements 14 and 16 can be moved translationally relative to one another in that damping elements 14 and 16 are rotated relative to one another.

[0062] If damping element 16 is moved translationally into the first direction relative to damping element 14 in the described manner, damping element 16, particularly an end wall 60, opposite damping part 52, of damping element 16, comes to rest in supportive contact with damping part 52. As a result, damping part 52 is elastically deformed, whereby motion energy, for example, is converted into deformation energy. Contact or edge changes and thus load changes can thereby be damped especially well. In contrast, if damping element 16 is moved translationally into the second direction relative to damping element 14 in the described manner, damping element 16, particularly an end wall 62, opposite damping part 56, of damping element 16, comes to rest in supportive contact with damping part 56. As a result, damping part 56 is elastically deformed, whereby motion energy, in turn, is converted into deformation energy. An especially advantageous contact or edge change damping can thereby be implemented. Through the use of damping parts 52 and 56, which are opposite one another, contact or edge change damping can be implemented, particularly on both sides. It should be particularly noted with such damping on both sides that contact or edge changes can be damped both in the first direction of rotation as well as in the second direction of rotation.