U.S. patent application number 14/772442 was filed with the patent office on 2016-02-04 for absorber-type vibration damper.
The applicant listed for this patent is Kyrill SIEMENS, Michael WIRACHOWSKI. Invention is credited to Kyrill SIEMENS, Michael WIRACHOWSKI.
Application Number | 20160033003 14/772442 |
Document ID | / |
Family ID | 50137651 |
Filed Date | 2016-02-04 |
United States Patent
Application |
20160033003 |
Kind Code |
A1 |
SIEMENS; Kyrill ; et
al. |
February 4, 2016 |
Absorber-Type Vibration Damper
Abstract
A tuned mass vibration damper (300), for example, for a
drivetrain of a motor vehicle, for damping a vibration component of
a rotational movement, includes at least three damper masses (110),
at least one guide component part (130) to movably guide the at
least three damper masses (110) such that the damper masses (110)
are arranged so as to be offset along a circumferential direction
(160) perpendicular to an axis of rotation (140) and can carry out
the oscillations, and a damping component part (310) rotatable
around the axis of rotation (140) of the rotational movement
opposite to the at least one guide component part (130) and which
comprises a support structure (340) and at least two damping
structures (350) connected to the support structure (340). The
damping structures (350) extend radially from the support structure
(340) and are constructed and arranged such that one damping
structure (350) of the at least two damping structures (350) when
making contact with one of two adjacent damper masses (110)
prevents a contact of the two adjacent damper masses (110).
Inventors: |
SIEMENS; Kyrill; (Wuerzburg,
DE) ; WIRACHOWSKI; Michael; (Wuerzburg, DE) |
|
Applicant: |
Name |
City |
State |
Country |
Type |
SIEMENS; Kyrill
WIRACHOWSKI; Michael |
Wuerzburg
Wuerzburg |
|
DE
DE |
|
|
Family ID: |
50137651 |
Appl. No.: |
14/772442 |
Filed: |
February 19, 2014 |
PCT Filed: |
February 19, 2014 |
PCT NO: |
PCT/EP2014/053206 |
371 Date: |
September 3, 2015 |
Current U.S.
Class: |
188/379 |
Current CPC
Class: |
F16F 15/145 20130101;
F16F 7/108 20130101 |
International
Class: |
F16F 15/14 20060101
F16F015/14; F16F 7/108 20060101 F16F007/108 |
Foreign Application Data
Date |
Code |
Application Number |
Mar 18, 2013 |
DE |
10 2013 204 711.8 |
Claims
1-15. (canceled)
16. A tuned mass vibration damper (300) for a drivetrain of a motor
vehicle for damping a vibration component of a rotational movement,
comprising: at least three damper masses (110) configured to carry
out an oscillation depending on the rotational movement to damp the
vibration component of the rotational movement; at least one guide
component part (130) configured to movably guide the at least three
damper masses (110) such that the damper masses (110) are arranged
so as to be offset along a circumferential direction (160)
perpendicular to an axis of rotation (140) of the rotational
movement and; a damping component part (310) rotatable around the
axis of rotation (140) of the rotational movement opposite to the
at least one guide component part (130), the damping component part
(310) comprising a support structure (340) and at least two damping
structures (350) connected to the support structure (340), the at
least two damping structures (350) extending radially proceeding
from the support structure (340) and being constructed and arranged
such that one damping structure (350) of the at least two damping
structures (350), when making contact with one of two adjacent
damper masses (110), prevents a contact of the two adjacent damper
masses (110) through an elastic deformation, and/or such that, when
a damper mass (110) of the at least three damper masses (110) makes
contact with a damping structure (350) of the at least two damping
structures (350), the damping component part is rotatable around
the axis of rotation (140) such that a further damping structure
(350) of the at least two damping structures (350) makes contact
with a further damper mass (110) of the at least three damper
masses (110).
17. The tuned mass vibration damper (300) according to claim 16,
wherein each of the damping structure (350) of the at least two
damping structures (350) comprises at least one damping portion
(420) constructed and arranged to elastically deform when making
contact with at least one of the adjacent damper masses (110).
18. The tuned mass vibration damper (300) according to claim 17,
wherein a damping structure (350) of the at least two damping
structures (350) further comprises at least one connection portion
(440) which connects the at least one damping portion (420) to the
support structure (340).
19. The tuned mass vibration damper (300) according to claim 17,
wherein a damping structure (350) of the at least two damping
structures (350) comprises a first damping portion (420-1) and a
second damping portion (420-2), wherein the first damping portion
is configured and arranged to make contact with a first of the at
least three damper masses (110), and wherein the second damping
portion is configured and arranged to make contact with a second
damper mass of the at least three damper masses (110) arranged
adjacent to the first damper mass (110).
20. The tuned mass vibration damper (300) according to claim 16,
comprising at least four damper masses (110) and at least two
damping component parts (310), wherein the damping component parts
(310) are arranged and configured such that each damper mass (110)
can make contact with a damping structure (350) of a different
damping component part (310) during a movement along a first
direction in circumferential direction (160) than during a movement
along a second direction opposite to the first direction.
21. The tuned mass vibration damper (300) according to claim 16,
wherein the support structure (340) is configured to connect the at
least two damping structures (350) to one another.
22. The tuned mass vibration damper (300) according to claim 16,
wherein the damping component part (310) is made of a plastic.
23. The tuned mass vibration damper (300) according to claim 16,
wherein the at least two damping structures (350) have a noise
reducing coating in an area in which they make contact with a
damper mass (110) during operation of the tuned mass vibration
damper (300).
24. The tuned mass vibration damper (300) according to claim 16,
wherein the support structure (340) is configured to support the
damping component part (310) so as to be rotatable relative to the
at least one guide component part (130).
25. The tuned mass vibration damper (300) according to claim 24,
wherein the damping component part (310) is configured to enable a
rotation of the damping component part (310) relative to the at
least one guide component part (130) by a maximum torsional angle
along the circumferential direction (160) of the rotational
movement and to prevent a rotation of the damping component part
(310) relative to the at least one guide component part (130) by an
angle exceeding the maximum torsional angle.
26. The tuned mass vibration damper (300) according to claim 16,
wherein the support structure (340) is configured to radially guide
the damping component part (310) through at least one guide
component part (130).
27. The tuned mass vibration damper (300) according to claim 26,
wherein the support structure (340) has an at least partially round
outer contour in a plane perpendicular to the axis of rotation
(140), and wherein the at least one guide component part (130) is
configured for radially guiding the damping component part (310)
and comprises, in the plane, an at least partially round outer
contour configured to cooperate with the outer contour of the
support structure (340) to carry out the radial guiding.
28. The tuned mass vibration damper (300) according to claim 26,
wherein the support structure (340) comprises at least one guide
structure (380), and wherein the at least one guide component part
(130) is configured to radially guide the damping component part
(310) and comprises at least one complementary guide structure
(400) configured to engage in the at least one guide structure
(380) so as to radially guide the damping component part (310).
29. The tuned mass vibration damper (300) according to claim 28,
wherein the at least one guide structure (380) and the at least one
complementary guide structure (400) are configured to permit a
rotation of the damping component part (310) relative to the at
least one guide component part (130) along a circumferential
direction (160) of the rotational movement by a maximum torsional
angle and to prevent a rotation of the damping component part (310)
relative to the at least one guide component part (130) by an angle
exceeding the maximum torsional angle.
30. The tuned mass vibration damper (300) according to claim 16,
wherein the damping component part (310) is not guided
radially.
31. The tuned mass vibration damper (300) according to claim 18,
wherein a damping structure (350) of the at least two damping
structures (350) comprises a first damping portion (420-1) and a
second damping portion (420-2), wherein the first damping portion
is configured and arranged to make contact with a first of the at
least three damper masses (110), and wherein the second damping
portion is configured and arranged to make contact with a second
damper mass of the at least three damper masses (110) arranged
adjacent to the first damper mass (110).
32. The tuned mass vibration damper (300) according to claim 16,
wherein the damping component part (310) is made of an injection
moldable plastic, and/or is made of a metallic material, so as to
form a combination of a metal ring and sprayed-on plastic.
33. The tuned mass vibration damper (300) according to claim 27,
wherein the support structure (340) comprises at least one guide
structure (380), and wherein the at least one guide component part
(130) is configured to radially guide the damping component part
(310) and comprises at least one complementary guide structure
(400) configured to engage in the at least one guide structure
(380) so as to radially guide the damping component part (310).
Description
PRIORITY CLAIM
[0001] This is a U.S. national stage of application No.
PCT/EP2014/053206, filed on Feb. 19, 2014. Priority is claimed on
the following application: Country: Germany, Application No.: 10
2013 204 711.8, Filed: Mar. 18, 2013, the content of which is/are
incorporated herein by reference in its entirety.
FIELD OF THE INVENTION
[0002] The present invention relates to a tuned mass vibration
damper such as can be used, for example, in a drivetrain of a motor
vehicle, i.e., for example, within the framework of a start-up
element of a motor vehicle, for damping a vibration component of a
rotational movement.
BACKGROUND OF THE INVENTION
[0003] In many areas of machine, plant and automotive engineering,
rotational irregularities occur when rotational movements are
transmitted. These rotational irregularities can result, for
example, when a rotational movement of this type is coupled into a
shaft or also due to changes in the amount of energy or torque
taken from the shaft and the rotational movement of the shaft.
[0004] An example of this is drivetrains of motor vehicles, i.e.,
for example, drivetrains of passenger cars, trucks or other utility
vehicles, in which an internal combustion engine is used as drive
motor. Because of its principle of operation, an engine of this
kind often has discontinuous torque peaks which are coupled into
its crankshaft or into another corresponding shaft and can possibly
lead to deviations with respect to a timing of the torque and/or
speed. Rotational irregularities of this kind can manifest
themselves as vibration components of a rotational movement, for
example.
[0005] Vibration dampers are used to keep such rotational
irregularities or vibration components of a rotational movement
away from other components of a complex mechanical system like a
drivetrain of a motor vehicle. These vibration dampers are intended
to eliminate the vibration components or at least reduce the
amplitude thereof. Thus, for example, in a drivetrain of a motor
vehicle within the framework of a start-up element which is
typically integrated between the internal combustion engine and a
downstream transmission in order to allow continued running of the
internal combustion engine also when the vehicle is stopped, during
which the transmission input shaft is likewise stationary.
[0006] Energy accumulator elements are often employed in vibration
dampers. These energy accumulator elements allow temporary
absorption and, therefore, buffering of energy peaks of the
rotational movement which are then coupled into the rotational
movement again at a later time. In many torsional vibration
dampers, the energy accumulators which are often configured as
spring elements are connected in the actual torque path, i.e., the
path of rotational movement, such that the rotational movement is
transferred via the energy accumulator elements.
[0007] In contrast, in tuned mass vibration dampers no transmission
of rotational movement takes place via the energy accumulator
elements. These tuned mass vibration dampers typically comprise one
or more damper masses which can carry out oscillations in a force
field to damp an unwanted vibration component of the rotational
movement. The force field is formed by the forces acting on the
damper masses. In particular, these forces also include a
centrifugal force in addition to the weight force.
[0008] Sharply diverging requirements are sometimes imposed on
corresponding tuned mass vibration dampers and the components
making up the latter. Foremost in this respect, apart from
functioning as efficiently as possible, are, for example, available
installation space, a production in the simplest possible manner
and lowest possible noise nuisance, to name only a few aspects. The
components surrounding the tuned mass vibration damper typically
allow only a limited installation space to be taken up by the tuned
mass vibration damper in all operating states. It should also be
producible in the simplest possible manner. Noise can also occur in
tuned mass vibration dampers because of operation, for example, due
to changes in the forces acting on the damper masses. As a result
of the latter, it can happen that the damper masses of the tuned
mass vibration damper are no longer guided with respect to the
movement thereof substantially by centrifugal forces, but rather by
the weight force acting upon them, for example, when a speed of the
rotational movement and, therefore, the influence of the
centrifugal forces decreases. Noises can occur when the damper
masses collide with each other or with other components, for
example, with the ends of their guide paths.
[0009] These noises, which are frequently metallic, can be
perceived by the driver and the passengers of the motor vehicle as
well as outside of the motor vehicle. These noises are frequently
perceived by persons as annoying because the occurrence of these
metallic noises is unexpected. For this reason, developers have
tried to reduce noise generation in a tuned mass vibration
damper.
[0010] DE 10 2011 100 895 A1 is directed to a centrifugal pendulum
absorber with a pendulum flange that is rotatable around an axis of
rotation and with a plurality of pendulum masses distributed along
the circumference on both sides of the pendulum flange. Two axially
opposed pendulum masses are connected to one another in each
instance by connection means extending through the pendulum flange
to form pairs of pendulum masses. In order to achieve an elastic
limiting of the pendulum masses without resorting to stop bumpers
and cutouts made for the latter in the pendulum flange, an elastic
limiting of an oscillating movement of the pendulum masses is
carried out in this case by means of an annular spring that is
integrated radially inside of the pendulum masses.
[0011] U.S. Pat. No. 6,382,050 relates to a vibration damping
device with a deflection mass arrangement which is arranged at a
base body which is rotatable around an axis of rotation having at
least one deflection mass and a deflection path which is associated
with the at least one deflection mass and along which the
deflection mass can move during the rotation of the base body
around the axis of rotation. The deflection path has a vertex area,
deflection areas on both sides of the vertex area, the distance of
these deflection areas from the axis of rotation decreasing from
the vertex area to the end areas of the deflection areas, and a
braking arrangement which is operative in the end areas of the
deflection areas and by means of which the movement of the at least
one deflection mass can be gradually decelerated when approaching
or reaching a respective end region of a deflection path.
[0012] This should be carried out through the simplest possible
constructional means so as to facilitate as far as possible not
only the availability of the necessary component parts but also the
assembly thereof in the form of the tuned mass vibration damper and
the components comprising the latter.
[0013] Therefore, there is a need for a better compromise between a
functioning of a tuned mass vibration damper, an efficient
utilization of installation space, reduced noise and the simplest
possible production of a tuned mass vibration damper.
SUMMARY OF THE INVENTION
[0014] A tuned mass vibration damper according to an embodiment
example for damping a vibration component of a rotational movement
which can be used, for example, in a drivetrain of a motor vehicle
comprises at least three damper masses which are configured to
carry out an oscillation depending on the rotational movement in
order to damp the vibration component of the rotational movement.
It further comprises at least one guide component part which is
configured to movably guide the at least three damper masses such
that the damper masses are arranged so as to be offset along a
circumferential direction perpendicular to an axis of rotation of
the rotational movement and can carry out the oscillation. Beyond
this, a tuned mass vibration damper according to an embodiment
example comprises a damping component part which is rotatable
around the axis of rotation of the rotational movement opposite to
the at least one guide component part and which comprises a support
structure and at least two damping structures connected to the
support structure, which damping structures extend radially
proceeding from the support structure and are constructed and
arranged such that one damping structure of the at least two
damping structures when making contact with one of two adjacent
damper masses prevents a contact of the two adjacent damper masses
through an elastic deformation. Alternatively or additionally, the
damping component part and damping structures thereof can also be
constructed in such a way that when a damper mass of the at least
three damper masses makes contact with a damping structure of the
at least two damping structures, the damping component part is
rotatable around the axis of rotation such that a further damping
structure of the at least two damping structures makes contact with
a further damper mass of the at least three damper masses.
[0015] Accordingly, a tuned mass vibration damper according to an
embodiment example is based on the insight that the aforementioned
compromise can be improved by using a damping component part of the
type described above. Due to the fact that this damping component
part is configured to be rotatable, it exerts less of an influence
on the oscillations of the damper masses under many operating
conditions so that the functioning of the tuned mass vibration
damper is barely affected. As will be shown in the following
description, the damping component part can be integrated in a
space-saving manner so as to take up only a slight additional
installation space. Moreover, due to the fact that the two adjacent
damper masses are prevented from touching by the damping component
part, noise development that is frequently perceived as unpleasant
is reduced. The additional or alternative effect of the damping
component part, whereby precisely as a result of one of its damping
structures making contact with a damper mass this damping component
part is rotatable or is rotated such that another one of its
damping structures makes contact with another damper mass, can lead
in this case to a limiting of the duration of coupling of damper
masses with one another. In this way, it can be possible optionally
to prevent a collision of the further damper mass so that annoying
noises can be prevented as far as possible or at least reduced.
Depending on the specific implementation of an embodiment example
and possibly depending on the intensity of contact, a deformation
of the damping structure and/or of the further damping structure
can result. Additionally or alternatively, a movement of the
further damper mass can also possibly be brought about by the
further damper mass making contact with the further damping
structure. Owing to the fact that the damping component part, in
that it has at least two damping structures, can interact with more
than only two damper masses, this can be achieved by technical
means which are simpler compared to many constructions and which
also negligibly complicate the assembly of the tuned mass vibration
damper.
[0016] Accordingly, in a tuned mass vibration damper according to
an embodiment example the damping structures can extend radially
between two adjacent damper masses. In other words, in this case
there exists a pitch circle around the axis of rotation with a
radius such that exactly one damping structure of the damping
component part is located along the pitch circle between the two
adjacent damper masses. For example, depending on specific
implementation or on the operating situation, the relevant damping
structure can possibly also be arranged or located only partially
between the two relevant damper masses.
[0017] Optionally, in a tuned mass vibration damper according to an
embodiment example the damping structures can comprise at least one
damping portion, respectively, which is constructed and arranged to
make contact with at least one of the adjacent damper masses and,
in doing so, to elastically deform. By elastic deformation is meant
a deformation that is detectable macroscopically, i.e., detectable
as such by the naked eye. Thus deformations which occur inevitably
substantially also when contact is made between materials which do
not count as elastically deformable are not taken into account.
Accordingly, depending on the embodiment example, an elastic
deformation is a deformation in which there is a dimensional change
of at least 0.1%, at least 1%, or at least 1%. In this way, it can
be possible optionally to selectively tune a damping characteristic
of the damping structures to the respective case of application of
the tuned mass vibration damper. For example, the force exerted by
the damping portions and, therefore, by the damping structures on
the damper masses can be determined and accordingly possibly
configured to be softer or milder by the shaping of the damping
portions and, therefore, taking into account the material from
which they are made, by the degree of elastic deformation.
Therefore, an impact behavior or a damping behavior can possibly be
selectively adjusted in this way through the damping portions.
Optionally, the damping portion can accordingly extend radially
from the support structure.
[0018] Additionally or alternatively, the damping portion can have
an outer contour in a plane perpendicular to the axis of rotation
that is circular segment-shaped, circular arc-shaped, circular,
elliptical arc-shaped, elliptical segment-shaped, ellipsoidal,
polygonal, rectangular, square, cross-shaped, U-shaped, V-shaped,
W-shaped, hook-shaped, web-shaped and/or curved. Accordingly, the
outer contour of the damping portion can optionally be
substantially constant along the axis of rotation. For example, it
can be shaped as a hollow cylindrical segment, hollow cylinder,
solid cylinder or solid cylindrical segment. Accordingly, in this
case, depending on the specific implementation, the damping portion
in a tuned mass vibration damper according to an embodiment example
can optionally be constructed as a hollow body or as a solid
body.
[0019] Further, in a tuned mass vibration damper according to an
embodiment example the damping structure can optionally further
have at least one connection portion which connects the at least
one damping portion to the support structure. The connection
portion can optionally also be elastically deformable. Depending on
the specific implementation, a corresponding connection portion can
be used for a more accurate positioning of the damping portion
and/or an additional elastic component can be integrated in the
damping structure for adapting the development of force of the
damping structure to the requirements imposed on the tuned mass
vibration damper according to an embodiment example in a broader
manner or also in a multi-stepped manner. In this way, it can be
possible optionally to achieve a better positioning of the damping
portions and/or a more multi-stepped force development of the
damping structures.
[0020] Optionally, in a tuned mass vibration damper according to an
embodiment example the connection portion can have an outer contour
in a plane perpendicular to the axis of rotation that is circular
segment-shaped, circular arc-shaped, circular, elliptical
arc-shaped, elliptical segment-shaped, ellipsoidal, polygonal
and/or web-shaped.
[0021] In addition to or as an alternative to this, the connection
portion can also optionally be constructed as a hollow body or as a
solid body. As has already been explained in connection with the
damping portion, it is optionally possible to achieve a more
selective adaptation of the development of forces to the
requirements set for the tuned mass vibration damper, e.g., a
smoother initiation of force delivery. For example, the connection
portion or connection portions can also be cylindrical or
cylindrical segment-shaped.
[0022] Additionally or alternatively in a tuned mass vibration
damper according to an embodiment example, the damping structure
can comprise a first damping portion and a second damping portion,
the first damping portion being configured and arranged to make
contact with a first damper mass, and the second damping portion
being configured and arranged to make contact with a second damper
mass arranged adjacent to the first damper mass. The first damper
mass and second damper mass are damper masses of the at least three
damper masses of the tuned mass vibration damper. In this way, it
can be possible optionally to implement a damping component part in
a way that economizes on installation space and, accordingly, to
improve the aforementioned compromise.
[0023] Optionally in an embodiment example of this type, the first
damping portion and the second damping portion can be connected to
one another only via the support structure. Likewise optionally and
in addition to or as an alternative to this, the first damping
portion and the second damping portion can face one another. In
this case, for example, the first damping portion and the second
damping portion can have a curved shape. Accordingly, in this case
the first damping portion and the second damping portion can
optionally have, for example, a circular arc-shaped and/or
elliptical outer contour in a plane perpendicular to the axis of
rotation and can be arranged in such a way that, when not loaded,
they substantially form segments of a common circle, a common
circular arc, a common ellipse or a common elliptical arc in the
plane.
[0024] Additionally or alternatively, a tuned mass vibration damper
according to an embodiment example can comprise at least four
damper masses and at least two damping component parts. The damping
component parts can be arranged and configured in such a way that
each damper mass can make contact with a damping structure of a
different damping component part during a movement along a first
direction in circumferential direction than during a movement along
a second direction opposite to the first direction. In other words,
in an embodiment example of this kind having at least four damper
masses and at least two damping component parts, an arrangement of
the damping structures of the at least two damping component parts
can be selected such that each of the damper masses makes contact
with a different damping component part during a movement along the
first direction than during a movement along the second direction,
wherein the first direction and the second direction run along the
circumferential direction of the rotational movement but are
oppositely directed. The word "direction" notwithstanding, the
individual "directions" may not necessarily refer to a direction in
the mathematical sense of a vector, but rather may be a line along
which the corresponding movement takes place. A line of this type
can be straight or curved. Directions which describe actual
directions along a line, for example, the movement direction, are a
separate case. Thus, for example, a first direction can be opposite
to a second direction, but both can run along or be directed along
a line which is also referred to as a "direction".
[0025] Accordingly, it can be possible to achieve a further
decoupling of the damper masses from one another without
significantly increasing production cost. Through the additional
decoupling of the damper masses from one another, it can be
possible optionally to lessen the influence on their ability to
oscillate and, accordingly, to less sharply limit, or even to
improve, the efficient damping of the vibration component of the
rotational movement. Accordingly, on the whole, the aforementioned
compromise can be further improved.
[0026] In a tuned mass vibration damper according to an embodiment
example comprising at least four damper masses and at least one
further damping component part, the latter can be arranged such
that a first damping structure of the further damping component
part can make contact with a first damper mass and a second damper
mass arranged adjacent to the first damper mass, and a second
damping structure of the further damping component part can make
contact with a third damper mass and a fourth damper mass arranged
adjacent to the third damper mass. In this case, a first damping
structure of the damping component part can make contact with the
first damper mass and the fourth damper mass arranged adjacent to
the first damper mass, and a second damping structure can make
contact with the second damper mass and a third damper mass
arranged adjacent to the second damper mass, Of course, an
arrangement of this kind can also be correspondingly expanded to
more than four damper masses and to more than two damping component
parts.
[0027] Two objects are adjacent to one another when no object of
the same type is arranged between them. Corresponding objects are
directly adjacent when they adjoin one another, i.e., for example,
contact one another. In this case, the adjacent arrangement refers
to an arrangement along the circumferential direction and not, for
example, along the axis of rotation. The damper masses can be
equidistant but can also be arranged along the circumferential
direction so as to diverge from an equidistant arrangement.
[0028] For example, if there are at least three damper masses
arranged adjacent to one another in an embodiment example, there is
always a damper mass having an adjacent damper mass along the
circumferential direction and opposite to the circumferential
direction.
[0029] The expressions employed herein to describe the arrangement
of the individual components, subassemblies and other objects
relative to one another always refer to the axis of rotation of the
rotational movement. The radial direction, also denoted simply by
"radially", is always perpendicular to, and faces away from, the
axis of rotation. In a corresponding manner, the axial direction,
also denoted simply by "axially", corresponds to the axis of
rotation, while the tangential direction, also referred to as
circumferential direction or denoted simply by "tangentially", is
perpendicular to both the axis of rotation and the radial
direction.
[0030] Additionally or alternatively in a tuned mass vibration
damper according to an embodiment example, the support structure
can be configured to connect the at least two damping structures to
one another. The damping component part can be a structural
component part that can be integrated in its entirety in the tuned
mass vibration damper so that it can be installed in a technically
simple manner. This can make it possible to facilitate the
production of the tuned mass vibration damper and, therefore, to
further improve the aforementioned compromise.
[0031] Additionally or alternatively, the damping component part in
a tuned mass vibration damper according to an embodiment example
can be formed in one part or integrally. For example, the damping
component part can be made of a plastic, i.e., an injection
moldable plastic, for example. Additionally or alternatively, it
can also be made of a metallic material, i.e., a plastic and a
metallic material, for example. Of course, it can also be
constructed as a structural component part comprising multiple
parts or pieces. However, the use of an injection moldable plastic
can make it possible in this case to produce the damping component
part by particularly simple technical means and, therefore,
inexpensively so that not only can it be produced in a simple
manner, but it can also be integrated in a simple manner into the
tuned mass vibration damper according to an embodiment example. By
component formed in one piece is meant a component that is made of
exactly one contiguous piece of material. A component or structure
made, provided or produced in one part or a component or structure
made, provided or produced integral with at least one further part
means that the component or structure cannot be separated from the
at least one further component without destroying or damaging one
of the at least two components concerned. Accordingly, a one-piece
structural component part is also at least a structural component
part which is formed integral with, or forms one part with, another
structure of the relevant structural component part.
[0032] Additionally or alternatively, in a tuned mass vibration
damper according to an embodiment example the damping structures
can have a coating in an area in which they make contact with a
damper mass during operation of the tuned mass vibration damper,
this coating being configured to reduce noise generation compared
to a mating of purely metallic materials. This can make it possible
to further improve noise development and, therefore, the
aforementioned compromise of regardless the material from which the
damping component part is made.
[0033] Additionally or alternatively, in a tuned mass vibration
damper according to an embodiment example the support structure can
be configured to support the damping component part so as to be
rotatable relative to the at least one guide component part. This
can make it possible to implement the damping component part so as
to economize on installation space. Optionally, the support
structure can comprise at least one circumferential portion which
extends in circumferential direction and which is substantially
annular, cylindrical, ring segment-shaped and/or cylinder
segment-shaped. Accordingly, a very compact implementation of the
damping component part can be realized. In a tuned mass vibration
damper of this type according to an embodiment example, the support
structure can also have, for example, at least two circumferential
portions and at least one substantially axially extending axial
portion, wherein the axial portion connects a first circumferential
portion to a second circumferential portion of the at least two
circumferential portions. Accordingly, depending on the specific
implementation, the support structure can allow, for example,
radial guiding at more than one guide component part insofar as
more than one guide component part is provided.
[0034] Optionally in a tuned mass vibration damper according to an
embodiment example, the damping component part can be configured to
enable a rotation of the damping component part relative to the at
least one guide component part by a maximum torsional angle along
the circumferential direction of the rotational movement and to
prevent a rotation of the damping component part relative to the at
least one guide component part by an angle exceeding the maximum
rotational angle. This can make it possible on the one hand to
allow a substantially free oscillation of the damper masses within
the maximum oscillating angle and on the other hand to implement a
defined, possibly low-noise stop by limiting the rotation to the
maximum torsional angle so as to prevent the damper masses from
colliding with one another or also to prevent one or more damper
masses from striking another structure which could also cause
noise. This can also have a positive influence on noise generation
and the aforementioned compromise can accordingly be improved.
[0035] As has already been mentioned, the support structure in a
tuned mass vibration damper according to an embodiment example can
additionally or alternatively be configured to radially guide the
damping component part through at least one guide component part.
This can ensure good operation of the tuned mass vibration damper
even under more extreme operating conditions, for example, during
extreme shaking.
[0036] Optionally, in a tuned mass vibration damper of this type
according to an embodiment example the support structure can have
an at least partially round outer contour in a plane perpendicular
to the axis of rotation. The at least one guide component part
which is configured for radially guiding the damping component part
can also have in the aforementioned plane an at least partially
round outer contour which is configured to cooperate with the outer
contour of the support structure to carry out the radial guiding.
An implementation which saves installation space can possibly be
realized in this way.
[0037] Additionally or alternatively, in a tuned mass vibration
damper according to an embodiment example the support structure can
have at least one guide structure. In this case, the at least one
guide component part which is configured to radially guide the
damping component part can have at least one complementary guide
structure which is configured to engage in the at least one guide
structure so as to bring about the radial guiding of the damping
component part. In other words, additionally or alternatively, the
radial guiding is brought about, or is at least supported, by the
interaction of the guide structure and complementary guide
structure of the support structure and the relevant guide component
part. Depending on the specific implementation, a tuned mass
vibration damper which is mechanically stable and/or economizes on
installation space can be realized in this way.
[0038] Optionally in a tuned mass vibration damper according to an
embodiment example the at least one guide structure and the at
least one complementary guide structure can be configured to allow
a rotation of the damping component part relative to the at least
one guide component part along a circumferential direction of the
rotational movement by the maximum torsional angle and to prevent a
rotation of the damping component part relative to the at least one
guide component part by an angle exceeding the maximum torsional
angle. To this end, the at least one guide structure and the at
least one complementary guide structure can optionally comprise a
recess and a projection which are configured to engage with one
another so as to bring about the radial guiding of the damping
component part, wherein a length of the projection along the
circumferential direction differs from a length of the recess by
the maximum torsional angle.
[0039] Optionally in a tuned mass vibration damper according to an
embodiment example, the guide structure of the damping component
part can be arranged at a guide portion which extends radially from
the support structure. The guide structure can optionally be
arranged so as to be radially inwardly located, radially centrally
located or radially outwardly located. In this way, it can be
possible, depending on design constraints, to make a better
compromise between a mechanical loading of the guide structure on
the one hand and the installation space conditions on the other
hand.
[0040] Alternatively, in an embodiment example of a tuned mass
vibration damper according to an embodiment example, it can also be
possible, of course, that the damping component part is not guided
radially, i.e., configured to be radially movable. This can have
the result that the damping component part can participate in a
radial movement so as to allow a freer movement of the damper
masses. The functioning of the tuned mass vibration damper can
possibly be further improved in this way. Therefore, the
aforementioned compromise can also possibly be improved in this
way. Additionally or alternatively, in a tuned mass vibration
damper according to an embodiment example the damping component
part can be configured to be guided by at least one guide component
part along the axis of rotation.
[0041] In a tuned mass vibration damper according to an embodiment
example, the damper masses can have at least one guide path,
respectively. The at least one guide component for the damper
masses can also have in each instance at least one guide path
corresponding to the guide paths of the damper masses. In this
case, the tuned mass vibration damper has in each instance at least
one rolling body for the damper masses, which rolling body is
configured to roll along the guide paths of the at least one guide
component part and along those of the damper masses in order to
guide them in such a way that a deflection of the damper masses out
of their respective center positions, also referred to as neutral
position, leads to a radial displacement of the center of mass of
the respective damper mass. It can be possible to implement a
speed-adaptive mass damper or tuned mass vibration damper in this
way.
[0042] A mechanical coupling of two components includes both a
direct coupling and an indirect coupling. A frictionally engaging
connection is brought about by static friction, a bonding
connection is brought about by molecular or atomic interactions and
forces, and a positively engaging connection is brought about by a
geometric connection of the relevant parts to be connected.
Accordingly, the static friction generally presupposes a normal
force component between the two parts to be connected.
[0043] A component can have an n-fold rotational symmetry, for
example, where n is a natural number greater than or equal to 2. An
n-fold rotational symmetry exists when the relevant component can
be rotated by (360.degree./n) around an axis of rotation or axis of
symmetry and substantially transitions into itself with respect to
shape, i.e., substantially self-maps in a mathematical sense after
a certain rotation. In contrast, a completely rotationally
symmetrical component substantially transitions into itself with
respect to shape when rotated by any amount and by any angle around
the axis of rotation or axis of symmetry, i.e., substantially
self-maps in a mathematical sense. An n-fold rotational symmetry
and a complete rotational symmetry are both referred to herein as
rotational symmetry.
[0044] As has already been mentioned, the above-mentioned features
can be implemented individually as well as in combination with each
other.
BRIEF DESCRIPTION OF THE DRAWINGS
[0045] Embodiment examples will be described and explained more
fully in the following with reference to the accompanying drawings
in which:
[0046] FIG. 1a shows a top view of a conventional tuned mass
vibration damper in a first operating state;
[0047] FIG. 1b shows the tuned mass vibration damper shown in FIG.
1a in a second operating state;
[0048] FIG. 2a shows a top view of a tuned mass vibration damper
according to an embodiment example;
[0049] FIG. 2b shows a cross section through the tuned mass
vibration damper shown in FIG. 2a;
[0050] FIG. 3a shows a top view of the tuned mass vibration damper
shown in FIGS. 2a and 2b according to an embodiment example in
which one of the two guide component parts is not shown;
[0051] FIG. 3b shows a perspective view of the tuned mass vibration
damper from FIGS. 2a, 2b and 3a in which a guide component part is
not shown;
[0052] FIGS. 4a, 4b and 4c show a top view and two side views of
the damping component part of the tuned mass vibration damper from
FIGS. 2a, 2b, 3a and 3b;
[0053] FIG. 4d shows a perspective view of the damping component
part from FIGS. 4a to 4c;
[0054] FIG. 5a shows a top view of a tuned mass vibration damper
according to an embodiment example in which the damper masses are
in a center position;
[0055] FIG. 5b shows an enlarged detail of the view in FIG. 5a;
[0056] FIG. 5c shows a top view of the tuned mass vibration damper
shown in FIGS. 5a and 5b according to an embodiment example when a
maximum torsional angle is reached;
[0057] FIG. 5d shows an enlarged detail from FIG. 5c;
[0058] FIG. 6a shows a top view of a tuned mass vibration damper
according to an embodiment example in which one of two guide
component parts is not shown, in a first operating state;
[0059] FIG. 6b shows the tuned mass vibration damper shown in FIG.
6a in a second operating state;
[0060] FIG. 6c shows a top view of the tuned mass vibration damper
from FIGS. 6a and 6b in a third operating state;
[0061] FIG. 6d shows a top view of the tuned mass vibration damper
shown in FIGS. 6a to 6c according to an embodiment example in a
fourth operating state;
[0062] FIG. 7a shows a perspective view of a damping component part
of a tuned mass vibration damper according to an embodiment
example;
[0063] FIG. 7b shows a perspective view of a further damping
component part of a tuned mass vibration damper according to an
embodiment example;
[0064] FIG. 7c shows a perspective view of a further damping
component part of a tuned mass vibration damper according to an
embodiment example;
[0065] FIGS. 8a, 8b, 8c show a top view, a side view and a
cross-sectional view through a damping component part of a tuned
mass vibration damper according to an embodiment example;
[0066] FIG. 8d shows a perspective view of the damping component
part shown in FIGS. 8a to 8c;
[0067] FIGS. 9a, 9b and 9c show a top view, a side view and a
cross-sectional view through a further damping component part of a
tuned mass vibration damper according to an embodiment example;
[0068] FIG. 9d shows a perspective view of the damping component
part shown in FIGS. 9a to 9c;
[0069] FIGS. 10a, 10b and 10c show a top view, a side view and a
cross-sectional view through a further damping component part of a
tuned mass vibration damper according to an embodiment example;
[0070] FIG. 10d shows a perspective view of the damping component
part shown in FIGS. 10a to 10c;
[0071] FIGS. 11a, 11b and 11c show a top view, a side view and a
cross-sectional view through a further damping component part of a
tuned mass vibration damper according to an embodiment example;
[0072] FIG. 11d shows a perspective view of the damping component
part shown in FIGS. 11a to 11c;
[0073] FIGS. 12a, 12b and 12c show a top view, a side view and a
cross-sectional view through a further damping component part of a
tuned mass vibration damper according to an embodiment example;
[0074] FIG. 12d shows a perspective view of the damping component
part shown in FIGS. 12a to 12c;
[0075] FIGS. 13a, 13b and 13c show a top view, a side view and a
cross-sectional view through a further damping component part of a
tuned mass vibration damper according to an embodiment example;
[0076] FIG. 13d shows a perspective view of the damping component
part shown in FIGS. 13a to 13c;
[0077] FIGS. 14a, 14b and 14c show a top view, a side view and a
cross-sectional view through a further damping component part of a
tuned mass vibration damper according to an embodiment example;
[0078] FIG. 14d shows a perspective view of the damping component
part shown in FIGS. 14a to 14c;
[0079] FIG. 15 shows a top view of a tuned mass vibration damper
according to an embodiment example in which a guide component part
is not shown and which comprises the damping component part shown
in FIGS. 14a to 14d;
[0080] FIG. 16 shows a fragmentary front view of a tuned mass
vibration damper according to an embodiment example;
[0081] FIG. 17a shows a top view of the tuned mass vibration damper
shown in FIG. 16 according to an embodiment example;
[0082] FIG. 17b shows a cross-sectional view through the tuned mass
vibration damper shown in FIG. 17a;
[0083] FIGS. 18a, 18b and 18c show a top view, a side view and a
cross-sectional view through a further damping component part of a
tuned mass vibration damper according to an embodiment example;
[0084] FIG. 18d shows a perspective view of the damping component
part shown in FIGS. 18a to 18c;
[0085] FIG. 19 shows a top view of a tuned mass vibration damper
according to an embodiment example with damper masses at maximum
deflection in which a guide component part is not shown;
[0086] FIG. 20a shows a fragmentary front view of the tuned mass
vibration damper from FIG. 19 in a first operating state;
[0087] FIG. 20b shows a view of the tuned mass vibration damper
comparable to FIG. 20a in a second operating state;
[0088] FIGS. 21a, 21b and 21c show a top view, a side view and a
cross-sectional view through a further damping component part of a
tuned mass vibration damper according to an embodiment example;
[0089] FIG. 21d shows a perspective view of the damping component
part shown in FIGS. 21a to 21c;
[0090] FIGS. 22a and 22b show a top view and a cross-sectional view
through a further damping component part of a tuned mass vibration
damper according to an embodiment example;
[0091] FIG. 22c shows a perspective view of the damping component
part shown in FIGS. 22a and 22b;
[0092] FIGS. 23a, 23b and 23c show a top view, a side view and a
cross-sectional view through a further damping component part of a
tuned mass vibration damper according to an embodiment example;
[0093] FIG. 23d shows a perspective view of the damping component
part shown in FIGS. 23a to 23c;
[0094] FIGS. 24a, 24b and 24c show a top view, a side view and a
cross-sectional view through a further damping component part of a
tuned mass vibration damper according to an embodiment example;
[0095] FIG. 24d shows a perspective view of the damping component
part shown in FIGS. 24a to 24c;
[0096] FIGS. 25a, 25b and 25c show a top view, a side view and a
cross-sectional view through a further damping component part of a
tuned mass vibration damper according to an embodiment example;
[0097] FIG. 25d shows a perspective view of the damping component
part shown in FIGS. 25a to 25c;
[0098] FIGS. 26a, 26b, 26c and 26d each show a top view of
different damping structures of damping component parts of tuned
mass vibration dampers according to an embodiment example;
[0099] FIGS. 27a, 27b and 27c show a top view, a side view and a
cross-sectional view through a further damping component part of a
tuned mass vibration damper according to an embodiment example;
[0100] FIG. 27d shows a perspective view of the damping component
part shown in FIGS. 27a to 27c;
[0101] FIG. 28a shows a cross-sectional view through a tuned mass
vibration damper according to an embodiment example with two of the
damping component parts from FIGS. 27a to 27d;
[0102] FIG. 28b shows a perspective view of the tuned mass
vibration damper from FIG. 28a in which one of the two guide
component parts is not shown; and
[0103] FIG. 28c shows a perspective view of the two damping
component parts of the tuned mass vibration damper from FIGS. 28a,
28b in a perspective view relative to one another.
DETAILED DESCRIPTION OF THE PRESENTLY PREFERRED EMBODIMENTS
[0104] Identical or comparable components are denoted by identical
reference numerals in the following description of the accompanying
drawings. Further, collective reference numerals are used for
components and objects which occur more than once in an embodiment
example or diagram but which are described collectively with
respect to one or more features. Components or objects which are
denoted by identical reference numerals or collective reference
numerals may be constructed identically or possibly also
differently with respect to one or more or all features, for
example, their dimensions, unless otherwise explicit or implicit
from the description.
[0105] As was already mentioned above, tuned mass vibration dampers
and other vibration dampers are used in many areas of machine,
plant and automotive engineering in which there are unwanted
vibration components when a rotational movement of a shaft is
generated, transmitted or utilized. These vibration components can
be reduced or even completely eliminated through the use of a
corresponding vibration damper.
[0106] For example, corresponding rotational irregularities can
occur in drivetrains of motor vehicles, i.e., for example,
drivetrains of passenger cars, trucks and utility vehicles, due,
for example, to the operating principle of an internal combustion
with a discontinuous power development owing to the combustion
process taking place in this internal combustion engine. The
rotational movement is transferred from the crankshaft via a
start-up element, which allows continued running of the internal
combustion engine even when the vehicle is stopped, to a
transmission input shaft or other input shaft of a component
downstream of the start-up element. The start-up element can be
based, for example, on a hydrodynamic clutch, a frictionally
engaging clutch or a combination of these two concepts.
[0107] Frictionally engaging contact exists when two objects enter
into frictionally engaging contact with one another such that a
force is formed therebetween in case of a relative movement
perpendicular to a contact surface, which allows a force, a
rotational movement or a torque to be transmitted. In this case,
there can be a difference in rotational speed, i.e., slip, for
example. Apart from this type of frictionally engaging contact, a
frictionally engaging contact also includes a frictionally engaging
connection between the relevant objects in which a corresponding
difference in rotational speed, or slip, essentially does not
occur.
[0108] A corresponding start-up element can be implemented, for
example, as a hydrodynamic converter with a lockup clutch.
[0109] Vibration dampers, which also include tuned mass vibration
dampers, have energy accumulator elements which are arranged and
configured such that they can absorb energy peaks which occur
during rotational irregularities and can couple them into the
rotational movement again at another time. In this way, the
unwanted vibration components are reduced or damped and possibly
even completely eliminated.
[0110] In tuned mass vibration dampers, the energy accumulator
elements are not included in the torque flow or transmission path
of the rotational movement. Rather, they are merely coupled with
the rotational movement by means of a flange and can accordingly
absorb the corresponding energy and release it again via the
flange.
[0111] The energy accumulator elements have damper masses which
move in a force field that is formed by the gravity force and the
centrifugal forces acting on the damper masses. Depending on the
operating state of the tuned mass vibration damper, these two
forces can be in a different proportion to one another in terms of
magnitude, which is why the damper masses may possibly collide with
one another or strike their end points in unfavorable operating
states. In conventional tuned mass vibration dampers, such events
are frequently perceived by a driver and passengers of a
corresponding motor vehicle, or even by passing pedestrians, as
unpleasant because they occur unexpectedly and may be accompanied
by consequently unpleasant noises. Since the relevant components
are usually made of a metallic material, the corresponding noises
are frequently metallic-sounding.
[0112] As will be shown in the following, it can be possible
through the use of an embodiment example of a tuned mass vibration
damper to prevent or at least reduce metallic noises which can
occur, for example, in normal driving operation as well as in crawl
operation of the vehicle and after the internal combustion engine,
also referred to as engine, has been switched off. Events of the
type described above can occur comparatively often precisely in
vehicles which are outfitted with an automatic engine stop-start
system.
[0113] For a more detailed illustration, FIGS. 1a and 1b show a top
view of a conventional tuned mass vibration damper 100 having four
damper masses 110-1, 110-2, 110-3 and 110-4 which are configured
precisely so as to carry out an oscillation depending on the
rotational movement that is coupled in via a flange region 120 in
order to damp a vibration component of the rotational movement. To
this end, the tuned mass vibration damper 100 in the form shown
here has two guide component parts 130, only one of which is shown
in FIGS. 1a and 1b for the sake of clarity. The flange region 120
is formed in the area of an axis of rotation 140 radially inside of
one of the guide component parts and correspondingly includes
therein a plurality of flange bores 150 for mechanically fastening
the tuned mass vibration damper 100 to another component.
[0114] The guide component parts 130 are configured to movably
guide the damper masses 110 in precisely such a way that they are
arranged so as to be offset along a circumferential direction 160
perpendicular to the axis of rotation 140 of the rotational
movement and can execute the oscillation. To this end, the damper
masses 110 and the guide component parts 130, which are also
referred to as guide plates owing to their plate-like construction,
have guide paths 170, only one of which, by way of example, is
designated by the relevant reference numeral in FIGS. 1a and 1b.
Since the damper masses 110 cover particularly the guide paths 170
in the guide component parts 130, they are also not visible in
FIGS. 1a and 1b.
[0115] The guide paths 170 of the damper masses 110 and of the
guide component parts 130 which are fixed with respect to rotation
relative to one another and so as to be spaced apart at fixed
distances along the axis of rotation 140 by a spacer connection in
the form of a plurality of spacer rivets 180 correspond to one
another. Accordingly, the guide paths 170 of the damper masses 110
and of the guide component part 130 are constructed substantially
identically, but are oriented in a mirror-inverted manner with
respect to one another so that when the damper masses are deflected
out of a center position a center of mass of the damper masses 110
is radially shifted. The guide paths 170 are substantially
kidney-shaped, i.e., have a continuous curved portion 190 and an
indented portion 200 opposite thereto.
[0116] In order to allow a guiding of the damper masses 110 through
the guide component parts 130, the tuned mass vibration damper 100
further has for each damper mass 110 at least one, in the present
case two, rolling bodies 210 which are constructed in this case as
stepped rollers 220.
[0117] In normal operation, the noises mentioned above can occur,
for example, when the damper masses 110, also referred to as
flyweights, strike the ends 230 of the guide paths 170. This can
happen, for example, when, as a result of occurring vibrations, the
damper masses 110 tend to have a greater oscillation amplitude than
is permitted by the maximum design oscillation angle, also referred
to as torsional angle, as is shown by way of example in FIG. 1a.
This results in a collision between the rolling bodies 210 and the
ends 230 of the relevant guide paths 170.
[0118] In this operating state, a centrifugal force 240 is
typically greater in magnitude than a weight force 250 acting on
the damper masses 110.
[0119] However, as is shown in FIG. 1b, this situation can change
when there is a decrease in speed of the rotational movement that
is coupled into the tuned mass vibration damper 100. For example,
after the engine is switched off, the rotational speed of the
transmission input shaft to which the tuned mass vibration damper
can be coupled so as to be fixed with respect to relative rotation
or so as to be rigid with respect to rotation can drop to zero. In
this case, however, as the speed of the transmission input shaft
decreases, the centrifugal force 240 acting on the damper masses
110 also decreases in magnitude. Accordingly, the damper masses 110
are subject to little or no radial constraints and/or constraining
forces. In this type of operating point or operating state, due to
the weight forces 250 acting on the damper masses, these damper
masses can possibly slide along their guide paths 170, also
referred to as paths, or can even drop.
[0120] Depending on the specific setting of the tuned mass
vibration damper 100 and guide component parts 130 thereof, the
damper masses 110 can strike their respective path ends 230 and/or
collide with one another as is illustrated by way of example in
FIG. 1b by collision point 260. This can cause a rattling noise
which is audible both inside and outside of the vehicle and which
is often found annoying.
[0121] Conventionally, this can be mitigated, for example, by
inserting plastic elements between the damper masses 110. But these
plastic elements can also fall out during unfavorable operating
states or because of faulty assembly. It is also conceivable to
mechanically couple the damper masses 110 to one another. However,
during operation, a damper mass can impede the freedom of movement
of the adjacent damper mass through this coupling. This can
possibly lead to a reduced functionality or functional
characteristic of the tuned mass vibration damper 100.
[0122] FIG. 2a shows a top view of a tuned mass vibration damper
300 according to an embodiment example of the present invention
which differs from the conventional tuned mass vibration damper 100
shown in FIGS. 1a and 1b substantially with respect to a damping
component part 310. Therefore, as regards the further components of
the tuned mass vibration damper 300, reference is made to the
description of tuned mass vibration damper 100. It is noted here
that it is possible, for example, that embodiment examples of a
tuned mass vibration damper 300 may differ in design from the
conventional construction described above. Accordingly, the guide
paths 170 can, of course, also be constructed differently than in
the preceding description. For example, it is possible to omit the
indentation or indented portion 200. Of course, different guide
path geometries can also be used optionally. Likewise it will be
appreciated that more than four or less than four damper masses 110
and a different quantity of guide paths 170, possibly having
differently shaped rolling bodies 210, can also be provided. It can
also be possible to implement damper masses 110 and guide component
parts 130 which make do entirely without any rolling bodies 210.
The rolling bodies can also possibly be formed integral with the
damper masses 110. As the above-mentioned examples show, embodiment
examples of a tuned mass vibration damper 300 are in no way limited
to the particulars of construction given in connection with the
drawings described thus far, which will also be demonstrated
particularly in the further description.
[0123] While exactly four damper masses 110 are implemented in the
present embodiment example, a different quantity of damper masses
110 can, of course, also be used in other embodiment examples
insofar as at least three damper masses 110 are distributed along
the circumferential direction. The individual damper masses can be
constructed so as to comprise one piece, one part or a plurality of
parts. In the present depicted embodiment, the damper masses 110
are formed of three individual damper masses 305 arranged adjacent
to one another along the axis of rotation 140. The individual
damper masses 305 are not fixedly connected to one another
mechanically in the implementation shown here, but rather can move
independently from one another owing to manufacturing tolerances or
other influences in the course of being guided through the guide
component parts 130. In this case, they are guided in common in the
guide paths 170 of the guide component parts 130 via the rolling
bodies 210, which are constructed as stepped rollers 220, and in
turn have their own guide paths 170 in each instance. Therefore,
the individual damper masses 305 may also be regarded as damper
masses 110, but are not arranged along the circumferential
direction 160 so as to be offset with respect to one another. This
distinguishes the individual damper masses 305 from the damper
masses 110 which are arranged in an offset manner along the
circumferential direction 160 and, therefore, so as to be
distributed along the circumference 160.
[0124] FIG. 2a shows a top view of the tuned mass vibration damper
300 according to an embodiment example which is comparable to FIG.
1a or 1b, but in which both guide components 130-1, 130-2 are
shown. FIG. 2b shows a sectional view along section line A-A
through the tuned mass vibration damper 300. In view of the
selected rendering in which a first guide component part 130
comprising the flange region 120 is shown on the left-hand input
side, the first guide component part 130 is also referred to as
left-hand guide component part or, in view of the implementation of
the guide path 170 and the plate-like configuration thereof, as
left-hand path plate. Correspondingly, a second guide component
part 130-2 which is arranged at an end of the tuned mass vibration
damper 300 on the side opposite the first guide component part 130
along the axis of rotation is also referred to as right-hand guide
component 103-2 or as right-hand path plate. As has already been
mentioned, the guide paths 170 in the embodiment example shown here
are also substantially kidney-shaped and are therefore also
referred to as kidney-shaped oscillating path or, for brevity,
kidneys. The guide component parts 130 are mechanically connected
to one another so as to be fixed with respect to relative rotation
by the spacer rivets 180, also referred to as spacer pieces or, for
brevity, rivets. Of course, in other embodiment examples,
techniques other than spacer rivets can be used for the mechanical
connection of the guide component parts 130. It is also possible to
implement fewer than two guide component parts 130, namely, for
example, only one individual guide component part. It may also
possibly be advisable to implement more than two guide component
parts.
[0125] It is noted here purely for the sake of completeness that
the flange bores 150, for example, in a hydrodynamic converter as
start-up element, can be used for mechanically connecting to a
torsional damper thereof which the hydrodynamic converter can
include in connection with its lockup clutch. In this case, the
corresponding bores or flange bores 150 can be used, for example,
for riveting the tuned mass vibration damper 300 to the relevant
torsional damper.
[0126] As has already been stated, the tuned mass vibration damper
300 according to an embodiment example, in contrast to the tuned
mass vibration damper 100 from FIGS. 1a and 1b, has the damping
component part 310 which can be made of plastic, for example, and
which is therefore also referred to as plastic ring. The damping
component part 310 in the present embodiment example is configured
substantially as an inner ring with a cup-shaped structure that
will be described in more detail referring to the further drawings.
The damping component part 310 is configured to be rotatable
relative to the guide component parts 130 around the axis of
rotation 140 of the rotational movement. The damping component part
310 is configured precisely in such a way that it allows the
damping component part 310 to rotate relative to the guide
component parts 130 by a maximum torsional angle along the
circumferential direction 160 of the rotational movement, but
prevents a rotation at an angle exceeding this maximum torsional
angle. In other words. the damping component part 310 can be
rotated selectively relative to the guide component part 130, the
damping component part 310 and guide component part 130 being
connected to one another so as to be fixed with respect to relative
rotation by the spacer rivets 180, by an angle that is less than
the aforementioned maximum torsional angle, but not by a greater
angle. For this reason, the damping component part 310 has cutouts
320 in a portion guided parallel to the flange region 150, which
cutouts 320 leave the flange bores 150 uncovered and are shaped
precisely in such a way that a mechanical connection, for example,
a corresponding rivet, which is also guided through the flange
bores 150 also does not come in contact with the damping component
part 310 at the maximum prevailing torsional angle. A mechanical
shearing load of the connection means in question, i.e., for
example, the rivets in question, can be prevented in this way.
However, it is, of course, also possible to utilize a corresponding
limiting of the torsional angle by the walls of the cutouts 320
making contact in a corresponding manner with the relevant
structures for fastening the tuned mass vibration damper 300 to
another subassembly.
[0127] Other constructional solutions for this purpose will be
described more fully in the course of the further description. For
example, the damping component part 310 can be made of an injection
moldable material which can make it possible to produce the guide
component part 130 in a particularly simple manner within the
framework of an injection molding process. Of course, other
plastics can also be used. Metallic materials can also be used in
addition or as an alternative, i.e., for example, metals, alloys or
metals or alloys supplemented by nonmetallic substances. Aside from
thermosets and thermoplastics, elastomers can also be used in their
entirety or in part as plastics, for example, for covering or
coating particular areas of the damping component part. In this
way, noise generation can optionally be reduced compared to a
purely metallic pairing of materials in case the damping component
part 310 contacts one of the damper masses 110.
[0128] While FIGS. 2a and 2b show a top view and sectional view of
a subassembly of a tuned mass vibration damper 300, also referred
to as speed-adaptive damper, with a damping component part 310
installed therein, FIGS. 3a and 3b show a top view and a
perspective view of the relevant damper assembly in which a
right-hand guide component part 130-2 is not visible.
[0129] As is also shown in FIGS. 3a and 3b, the damping component
part 310 has a substantially cup-shaped construction with a central
recess 330 that extends substantially perpendicular to the axis of
rotation 140 and accordingly forms a "hole" in a base of the
cup-shaped construction.
[0130] Further, the damping component part 310 has a support
structure 340 and at least two damping structures extending
radially from the support structure 340, there being a total of
four damping structures 350-1, 350-2, 350-3 and 350-4 in the
present embodiment example. In other embodiment examples, there can
also be a larger or smaller quantity of damping structures 350,
also referred to as driver elements, than the four damping
structures 350 implemented in this case. These damping structures
350 are configured and arranged in such a way that one of the
damping structures 350 in each instance prevents contact between
two adjacent damper masses 110 through elastic deformation when
making contact with one of the two adjacent damper masses 110.
[0131] Additionally or alternatively, the damping component part
310 can also produce a different or further effect. In particular,
precisely when one of its damping structures 350 makes contact with
a damper mass 110, this damping component part 310 can be
rotatable, or can be rotated, in such a way that another one of its
damping structures 350 makes contact with another damper mass 110.
This can result in a temporary coupling of the damper masses 110
with one another, by means of which a striking of the further
damper mass 110 can be prevented so that an annoying noise can be
prevented or at least reduced. Depending on the specific
implementation of an embodiment example and possibly depending on
the intensity with which contact is made, a deformation of the
damping structure 350 and/or of the further damping structure 350
can take place. Additionally or alternatively, a movement of the
further damper mass 110 can possibly also take place when the
further damper mass 110 makes contact with the further damping
structure 350. For example, if the tuned mass vibration damper 300
has an even-number quantity of damper masses, the damper mass 110
and further damper mass 110 can be located opposite one another. Of
course, similar and/or different arrangements of these two damper
masses 110 are also possible in tuned mass vibration dampers with
either even or odd numbers.
[0132] Whereas the quantity of damping structures 350 of the
damping component part 310 is at least two and the quantity of
damper masses 110 of the tuned mass vibration damper 300 is at
least three, i.e., both can essentially have any greater quantity
independent from one another, it may possibly be advisable to
select a total quantity of damping structures 350 of the tuned mass
vibration damper 300 that corresponds to the number of damper
masses 110. In so doing, it is not necessary that the damping
structures 350 belong to a single damping component part 310. On
the contrary, a plurality of damping component parts 310 can also
be used in connection with a tuned mass vibration damper 300 of
this type. In this connection, it is relevant only that only
exactly one damping structure 350 which is configured exactly as
was described above is arranged between two adjacent damper masses
110. It can have one damping portion, but can also have a plurality
of damping portions. A damping structure 350 is arranged between
two adjacent damper masses 110 precisely when there is a
corresponding pitch circle which intersects the two damper masses
110 in question and precisely the one damping structure 350 is
arranged therebetween along the relevant pitch circle.
[0133] The support structure 340 serves inter alia to connect the
damping structures 350 to one another. To this end, the support
structure in the damping component part 310 of a tuned mass
vibration damper 300 shown here is annular or cylindrical. The
support structure 340 accordingly forms a wall of the cup-shaped
structure of the damping component part 310. Depending on the
specific implementation of a corresponding damping component part
310, however, the support structure 340 can also be shaped
differently as will be explained in the following. For example, it
can have only one circumferential portion 360 which extends along
the circumferential direction 160 and which is only partially
annular or cylindrical, i.e., ring segment-shaped or cylinder
segment-shaped. A corresponding circumferential portion 360 can
also possibly have a different geometric shape in another damping
component part 310.
[0134] Depending on the specific embodiment, the support structure
340 can also serve, for example, to support the damping component
part 310 rotatably relative to at least one of the guide component
parts 130 or, in case of only a single guide component part 130,
can serve to support the damping component part 310 rotatably with
respect to the latter. In this regard, the geometric shape of the
support structure 340 described above can serve this purpose, for
example. In other words, the support structure 340 can have an at
least partially round outer contour in a plane perpendicular to the
axis of rotation 140.
[0135] Further, a radial guiding of the damping component part 310
in cooperation with at least one of the guide component parts 130,
or the guide component part 130 insofar as only one guide component
part 130 is implemented, can also be associated with the rotatable
support. The support structure 340 can also serve this purpose.
Accordingly, in this case, for example, the support structure 340
can have an at least partially round outer contour in a plane
perpendicular to the axis of rotation 140. In this case, the guide
component part 130 which is used for radially guiding the damping
component part 310 can also have an at least partially round outer
contour in the same plane so that this outer contour can cooperate
with the outer contour of the support structure 340 precisely so as
to bring about the radial guiding.
[0136] Additionally, however, the embodiment example shown here has
guide structures which are arranged at guide portions 370 in the
damping component part 310 shown here and which will be described
more fully referring to the further drawings. Two adjacent guide
portions 370 in each instance form the cutouts 320 in a base region
of the cup-shaped structure of the damping component part 310.
[0137] As can be seen from FIGS. 2a, 2b, 3a and 3b, the damping
component part 310, also referred to as ring, is located between
the two guide component parts 130-1, 130-2 in the tuned mass
vibration damper 300 illustrated here. Accordingly, the damping
component part 310 is held in axial direction, i.e., along the axis
of rotation 140. In other words, the damping component part 310 is
configured precisely such that it is guided through the guide
component part 130, or guide component parts 130, along the axis of
rotation 140.
[0138] The support of the ring in radial direction, i.e., the
radial guiding thereof, can be implemented through the shape of the
support structure 340 as well as through guide structures which can
be arranged, for example, at the guide portions 370. However, the
guide portions 370 and the corresponding guide structures represent
optional components that can be omitted, as the case may be, owing
to the positive engagement between the damping component part 310
and first guide component part 130-1 (left-hand plate path). As
will be shown in more detail in the further description, the
damping component part 310 is rotatably supported and can rotate by
a defined angle, namely, within the maximum torsional angle.
[0139] FIGS. 4a, 4b, 4c and 4d, respectively, show the damping
component part 310 of the tuned mass vibration damper 300 from
FIGS. 2a, 2b, 3a and 3b in a top view, two side views and a
perspective view. FIGS. 4a to 4d again show the substantially
cup-shaped structure of the damping component part 310 with its
support structure 340 which extends around the axis of rotation
140, substantially in the shape of a hollow cylinder, as outer wall
of the cup-shaped structure. FIGS. 4a to 4d also show the central
recess 330 and the four damping structures 350-1, 350-2, 350-3 and
350-4 as well as a total of five guide portions 370 which extend
radially, in the present case radially inwardly, from the support
structure 340. A guide structure 380, here shaped as a projection
390, is arranged in each instance at the guide portions 370 at a
side facing the first guide component part 130-1 (not shown in
FIGS. 4a to 4d). The projections, also referred to as guide noses
in view of their shape and function, are aligned and arranged
precisely in such a way that they can engage in corresponding
recesses or cutouts in the relevant guide component part 130 in
order to bring about the radial guiding of the damping component
part 310. Accordingly, the support of the damping component part
310 in radial direction is carried out in the damping component
part 310 shown here by means of the guide structures 380 which are
implemented as projections 390 and which are guided in
corresponding complementary guide structures in the form of
recesses or cutouts in the guide component part 130. This is also
shown in FIGS. 5a to 5d. Of course, the arrangements of projections
390 and recesses can also be reversed.
[0140] FIG. 5a shows a top view of the tuned mass vibration damper
300, already described above referring to FIGS. 2a to 4d, from the
side of the first guide component part 130-1 in which the damper
masses 110 are in a center position. In a corresponding manner, the
rolling bodies 210 are also arranged substantially in the center of
the guide path 170 in the area of the deepest indentation of the
indented portion 200.
[0141] FIG. 5b shows an enlarged area of the region designated by a
circle A in FIG. 5a. This illustrates how the guide structure 380
implemented as projection 390 engages in a corresponding
complementary guide structure 400 which is implemented as recess
410 and accordingly enables the radial guiding of the damping
component part 310.
[0142] Recess 410 extends over a length or angular area which
differs by the maximum torsional angle from a length or angular
area along which the projection 390 extends. Accordingly, in the
damping component part 310 shown here, the recess 410 in the first
guide component part 130-1 extends at the maximum torsional angle
along the circumferential direction 160 more than the projection
390 of the damping component part 310 extends along the
circumferential direction 160.
[0143] While FIGS. 5a and 5b show the situation of the tuned mass
vibration damper in which the damper masses 110 are in the center
position and the guide structure 380 is also arranged
correspondingly substantially centrally in the complementary guide
structure 400, FIGS. 5c and 5d show views comparable to FIGS. 5a
and 5b in which the damper masses 110 are in a state of maximum
deflection and the rolling bodies 210 have approached the ends 230
of the guide paths 170. However, the guide structures 380 in
cooperation with the complementary guide structures 400 prevent the
rolling bodies 210 from making contact with the ends 230 of the
guide paths 170. On the contrary, in the embodiment example of a
tuned mass vibration damper 300 shown here, the guide structures
380 make contact with the complementary guide structures 400 and
accordingly limit the maximum torsional angle of the damping
component part 310 relative to the guide component parts 130 so
that--through the agency of the damping structures 350--the rolling
bodies 210 can likewise be prevented from striking the ends 230 of
the guide paths 170. FIG. 5d shows how the guide structure 380
strikes a left-hand end of the complementary guide structure 400
before the rolling bodies 210 in FIG. 5c reach the ends 230 of the
guide paths 170.
[0144] The configuration of the damping structures 350 in the
present embodiment example will be described more fully referring
once more to FIGS. 4a to 4d in order to further explain the
interaction between the damping structure 350 and the damper
masses. In the damping component part 310 shown here, the damping
structures 350 comprise two damping portions 420-1, 420-2. In the
damping component part 310 shown here, these two damping portions
420-1, 420-2 extend radially from the support structure 340 and are
configured and arranged to make contact with at least one of the
adjacent damper masses 110 (not shown in FIGS. 4a to 4d) and, in so
doing, to deform elastically. The damping portions 420 have a
circular-arc segment-shaped outer contour in a plane perpendicular
to the axis of rotation 140 as is shown in FIG. 4a, for example.
The outer contour remains substantially constant with respect to
its shape and dimensioning along the axis of rotation 140.
[0145] In the damping component part 310 shown here, the two
damping portions 420-1, 420-2 are connected to one another only
through the support structure 340. There is no interconnection. The
two circular-arc segment-shaped damping portions 420-1, 420-2 face
one another, i.e., are curved, such that they substantially form
segments of a common circle or circular arc in the above-mentioned
plane perpendicular to the axis of rotation 140 in substantially
load-free state as is shown in FIGS. 4a to 4d.
[0146] The first and second damping portions 420-1, 420-2 of the
relevant damping structure 350 are configured and arranged in
precisely such a way that the first damping portion 420-1 can make
contact with a damper mass 110 arranged adjacent to it along
circumferential direction in a first direction, while the second
damping portion 420-2 can make contact with a damper mass 110
arranged adjacent to it along the circumferential direction 160 in
the opposite direction. In this way, it can be possible optionally
to provide a very compact but nevertheless mechanically stable and
sturdy damping structure 350 with only a small radially outward
profile. Depending on the specific implementation, it can possibly
be advisable that the damper masses 110 are also constructed with a
corresponding outer contour adapted to the geometry of the damping
portions 420 in a corresponding area in which they make contact
with the damping portions 420. In other words, it can possibly be
advisable that the damper masses 110 are also formed with a
cylindrical segment-shaped outer contour in such an area.
[0147] Due to the fact that the damping structures 350 or damping
portions 420 thereof can possibly support the damper masses during
operation, they are also referred to as supporting brackets.
[0148] In terms of function, therefore, the function performed by
the damping component part 310 consists in that the damper masses
110 are supported relative to one another. In this way, it can be
possible optionally to bring about a damping of the damper masses
110 in or before their stops. It can also be possible optionally to
keep the damper masses 110 spaced apart through the support of the
damper masses 110 relative to one another so that the damper masses
110 can be prevented from colliding with one another, which can
happen, for example, when switching off the engine. This can have
the result that the rattling noises no longer occur at all or, as
the case may be, are at least damped to the extent that they are
barely perceptible, if at all, inside or outside the vehicle.
[0149] Accordingly, in contrast to other solutions, a guiding of
the damper masses 110 and a damping of the noises that are possibly
generated by them can possibly be realized independently from
spacer pieces, i.e., for example, rivets. In this way, it can be
possible optionally to implement new design possibilities with
respect to the constructional layout of the damping component part
310. In this connection, a significant aspect of the damping
component part 310 is its rotatable bearing support which can
prevent, or at least inhibit, the damper masses 110 from jamming in
or adhering to the damping component part 310.
[0150] Accordingly, a free oscillation angle of the damper masses
110 can optionally be defined through the proportions and
geometries of the damping structures 350 and damping portions 420
thereof. On the other hand, properties such as stiffness and
damping can possibly be realized through a suitable geometry or a
suitable choice of material. Owing to the rotatable bearing support
of the damping component part 310, a free oscillation of the damper
masses 110 within the defined angle is not impeded.
[0151] FIGS. 6a, 6b, 6c and 6d show views of the tuned mass
vibration damper 300 comparable to FIG. 3a under various conditions
to illustrate functioning in various operating states of the tuned
mass vibration damper 300 according to an embodiment example. FIG.
6a shows a situation similar to that in FIG. 3a. This is a
situation that can occur, for example, during engine operation.
During normal operation of this type, the centrifugal force 240
acting on the damper masses 110 is generally substantially higher
in magnitude than a corresponding weight force component 250.
Therefore, the damper masses 110 are retained radially outward and
move along their guide paths 170 corresponding to the existing
excitation. FIG. 6a shows a situation in which the damper masses
110 are arranged in their center positions as has already been
shown in FIG. 3a.
[0152] Whereas the damping portions 420 do not contact the damper
masses 110 in the situation shown in FIG. 6a, all of the damper
masses 110 are deflected along the same direction in the situation
illustrated in FIG. 6b. As a result, the damper masses 110 make
contact with the corresponding damping portions 420, i.e., for
example, the first damper mass 110-1 makes contact with the first
damping portion 420-1. Therefore, the damping component part 310 is
rotated. A significant elastic deformation of the damping portions
420 or of the damping structure 350 does not occur, although, of
course, an elastic deformation that is detectable macroscopically
occurs here as well.
[0153] In the situation in FIG. 6b, the tuned mass vibration damper
300 is shown with damper masses 110 deflected to the maximum
extent, i.e., at maximum oscillation amplitude. Before the damper
masses 110 can go into the stops of their guide paths 170 which are
formed by the corresponding path ends 230, they are supported
relative to one another by means of the damping structures 350 or,
in the present embodiment example, by means of the damping portions
420 of the damping structures 350. In doing so, the damping
component part 310 rotates slightly. In addition, the oscillation
angle can optionally be limited by means of the guide structures
380 and corresponding complementary guide structures 400 (not shown
in FIGS. 6a to 6d), i.e., the guide noses and corresponding guides
of the guide component parts 130 as was illustrated, for example,
in FIGS. 5a to 5d. As has already been mentioned, FIGS. 5a to 5d
show the torsional vibration damper 300 in a rear view in which the
first guide component part 130-1 of the damper assembly faces
forward. The guiding of the damping component part 310 in
circumferential direction 160 is shown in the two detailed views in
FIGS. 5b and 5d.
[0154] Again for the sake of clarity, the second guide component
part 130-2 is not shown in FIGS. 6a to 6d.
[0155] FIGS. 6c and 6d show a second state in which the engine is
switched off, wherein the transmission input shaft continues to run
due to its inertia. A similar situation can also take place during
a crawl operation of the vehicle, for example.
[0156] During slow crawling, the transmission input shaft typically
rotates at a lower speed than engine speed. In such a case, unlike
in normal operation of the engine as was shown in FIGS. 6a and 6b,
the weight force 250 of the damper masses 110 is appreciably
greater in magnitude in this state than the corresponding component
of centrifugal force 240.
[0157] The situation is similar when switching off the engine. The
transmission input shaft continues to run for several seconds.
After a certain time, the amount of weight force 250 exceeds that
of the opposed centrifugal force component 240 as is shown in FIGS.
6c and 6d. In the absence of appropriate steps, the damper masses
110 would fall uncontrolledly into the stops, i.e., the ends 230 of
the guide paths 170, as has already been mentioned and described in
connection with FIGS. 1a and 1b.
[0158] In both states, the damping component part 310 ensures that
the damper masses 110 are kept apart so that no collisions are
possible. In other words, the damping structures 350 prevent
contact between adjacent damper masses 110.
[0159] Further, the damping component part 310 holds the damper
masses 110 in their radial position and accordingly prevents the
damper masses 110 from striking the rolling bodies 210 in radial
direction.
[0160] As is shown in FIG. 6c, for example, the second damper mass
110-2 and the third damper mass 110-3 have dropped down and come
into contact with the damping portions 420 of the relevant damping
structure 350 arranged below. The first damper mass 110-1 and the
fourth damper mass 110-4 also drop down due to the weight force and
are intercepted by the corresponding damping portions 420 of the
damping structures 350 arranged on the left-hand side and
right-hand side referring to FIG. 6c in time to prevent their
rolling bodies 210 from striking the ends 230 of the guide paths
170. The damping structure 350 arranged at the top in FIG. 6c is in
a non-tensioned state.
[0161] FIG. 6d shows a situation in which the second damper mass
110-2 is in its center position and--as the correspondingly lowest
damper mass 110 due to the weight force 250--does not mechanically
load the damping portions 420 of the damping structures 350
arranged adjacent thereto in both circumferential directions 160.
However, the situation is different with respect to the first
damper mass 110 and the third damper mass 110-3 which mechanically
loads a corresponding damping portion 420 of the two damping
structures 350 mentioned above. Owing to a slight rotation, the
fourth damper mass 101-4 has also not come to a halt in its center
position, but rather has moved in direction of a maximum
deflection. Also because of this, one of the relevant damping
portions 420 of one of the damping structures 350 has made contact
with the relevant fourth damper mass 101-4.
[0162] As far as the question of guiding in circumferential
direction and radial support, the tuned mass vibration damper 300
implemented in the above-described embodiment example of a tuned
mass vibration damper 300 is precisely one in which the guide
structure 380 is arranged substantially centrally on the guide
portions 370. However, other appropriate implementations can also
be selected as will be explained more fully, for example, in
connection with FIGS. 7a, 7b and 7c.
[0163] In principle, the guide structures 380, i.e., for example,
projections 390, can be positioned in any way on the guide portions
370. Accordingly, for example, the guide structures 370 can be
arranged radially inwardly as is shown in FIG. 7a, radially
outwardly at the support structure 340 as is shown in FIG. 7b, or
centrally on the guide portions 370 as is shown, for example, in
FIG. 4d. Where appropriate, the guide structures can also be
entirely omitted as is shown, for example, in FIG. 7c. A radial
support of the damping component part 310 is carried out in this
case by a positive engagement with at least one of the guide
component parts 130, i.e., for example, the first guide component
part 130-1, as was already shown referring to FIG. 2b.
[0164] Therefore, depending on the specific implementation, it is
also possible to dispense with the guide portions 370. The latter
have no function at least with respect to the question of receiving
guide structures 380 with respect to those of the damping component
parts 310 shown in FIGS. 7b and 7c. For example, in the damping
component part 310 shown in FIG. 7b, the guide structures 370 are
arranged directly at the support structure 340, while the damping
component part 310 in FIG. 7c has no corresponding guide structures
380 at the damping component part 310.
[0165] As regards the question of implementation of the damping
structures 350, the embodiment examples shown thus far have only
been those in which exactly two damping portions 420 were
implemented for each damping structure 350. Of course, other
embodiment examples can diverge from this. For example, a damping
structure 350 can also include only one single guide portion 420 or
possibly also a plurality of guide portions 420. FIGS. 8a to 14d
show various embodiments of damping component parts 310 in which
further variants of corresponding damping structures 350 are
implemented. Correspondingly, in order to achieve aimed-for
characteristics which may include, for example, a determined
damping characteristic or a determined resiliency, the damping
portions 420 of the damping component part 310 can, for example, be
coated or formed of a different material such as a rubber or other
elastomer, for example. In principle, the damping portions 420 and
associated damping structures 350 can be implemented in any form.
Some of the possible forms are shown in FIGS. 8 to 14, wherein
drawing parts a show a top view, drawing parts b show a side view,
drawing parts c show a cross-sectional view along a cross section
plane A-A running through the axis of rotation 140, and drawing
parts d show a perspective view of the relevant damping component
parts 310. The following description will essentially focus on the
differences compared to the embodiment forms described above.
[0166] FIGS. 8a to 8d show a damping component part 310 in which
there are no guide structures 380 provided at the guide portions
370 as was already shown, for example, in FIG. 7c. The damping
structures 350 have exactly one damping portion 420 having a
circular arc-shaped cross section in a plane perpendicular to the
axis of rotation 140. Accordingly, in view of the circular arc
shape, this is a damping component part 310 in which the damping
portion 420 or damping structure 350 is formed as a hollow body. In
this way, it can be possible optionally to realize greater
elasticity or a reduced force delivery compared to a solid-body
implementation.
[0167] FIG. 9 shows a further damping component part 310 which
differs from that described referring to FIG. 8 in that it has no
guide portions 370 extending radially, in the present case radially
inwardly, from the support structure 340 toward the axis of
rotation 140.
[0168] FIG. 10 shows a further damping component part 310 which
differs from that shown in FIG. 9 essentially in that the support
structure 340 in this case has a plurality of circumferential
portions 360 which connect the damping portions 420 of the damping
structures 350 to one another and which are substantially ring
segment-shaped or hollow-cylindrical segment-shaped in each
instance. Owing to the fact that this damping component part 310 is
also intended for four damper masses 110, the support structure 340
correspondingly has four circumferential portions 360 which join
the relevant damping portions 420 to one another, but without
bridging them. In other words, in this damping component part 310 a
direct straight line can be drawn starting from the axis of
rotation 140 so as to intersect the damping portions 420 without
first passing the support structure 340. Accordingly, FIG. 10 shows
a configuration of the damping component part 310 in which the
support structure 340 is not a contiguous structure but rather is
made up of individual portions, namely, circumferential portions
360.
[0169] FIG. 11 shows a further embodiment of a damping component
part 310 which is similar to the damping component part 310 from
FIGS. 8a to 8d. In this case too, the support structure 340 again
has guide portions 370, but the damping structures 350 are
constructed differently. The damping structures 350 have a damping
portion 420 which has essentially a web-shaped outer contour and is
formed as a solid body. The web extends substantially along a
radial direction away from the axis of rotation 140. The web-like
structure is constructed so as to be rounded at a radially
outwardly located region, and a contour of the damping portions 420
or damping structures 350 does not substantially change, i.e., is
constant, along the axis of rotation 140.
[0170] FIG. 12 shows a further damping component part 310 which
differs in two features from that shown in FIG. 11. For example,
the guide portions 370 do not extend as far radially inward as was
the case with the damping component part 310 from FIG. 11. Beyond
that, the damping structures 350 are no longer web-shaped but,
instead, there are two damping portions 420-1, 420-2 which are each
formed as hollow-cylindrical structures. The latter are directly
connected to the support structure 340 which is in turn formed as
an annular or hollow-cylindrical structure. The two substantially
hollow cylindrical damping portions 420-1, 420-2 are arranged and
oriented so as to be mirror-symmetrical to corresponding symmetry
planes 430.
[0171] In this case, in contrast to the embodiment examples
described above in which the damping portions 420 are not connected
to one another otherwise than through the support structure 340,
the two damping portions 420 are also directly connected to one
another and accordingly form a figure-8 structure which is arranged
at a 90-degree rotation to the support structure 340 with respect
to a radial direction. An outer contour and an inner contour of the
relevant damping portions 420 and, therefore, of the damping
structure 350 along the axial direction 140 essentially do not
change. Of course, this may differ in other embodiment
examples.
[0172] FIG. 13 shows a further damping component part 310 which
differs from that in FIG. 9 essentially in that the damping portion
420 is no longer connected directly to the support structure 340.
While the damping portion 420 is also substantially
hollow-cylindrical segment-shaped or ring segment-shaped in this
case also, the ends in circumferential direction 160 no longer
merge directly in the support structure 340. Rather, this damping
component part 310 has a connection portion 440 which is web-shaped
and faces radially away from the axis of rotation 140 while
connecting the damping portion 420 to the support structure 340
symmetrical to the planes of symmetry 430. In this way, it can be
possible optionally to further increase a flexibility of the
damping structure 350 compared to the embodiment shown in FIG. 9 in
that the damping portions 420 are now no longer directly connected
to the support structure 340 but rather via the connection portions
440. Accordingly, the damping portions 420 in this damping
component part 310 no longer have two connections to the support
structure 340 but rather only one which can optionally have a
greater flexibility with respect to a shearing movement owing to
its elongated shape.
[0173] Finally, FIG. 14 shows a further damping component part 310
which differs from the damping component part 310 shown in FIG. 13
in that the connection portions 440 are no longer web-shaped but
rather are in turn also hollow-cylindrical or circular arc-shaped
in a corresponding plane perpendicular to the axis of rotation 140.
In this way, it can be possible optionally to achieve increased
stiffness with respect to a shearing deformation of the damping
portions 420 compared to the damping component part 310 from FIG.
13.
[0174] FIG. 15 shows a view of a tuned mass vibration damper 300
comparable to FIG. 3a in which the damping component part 310
described in connection with FIG. 14 is implemented instead of the
damping component part 310 described in FIG. 3a. Here again, the
second guide component part 130-2, also referred to as right-hand
path plate, is not shown in the interest of greater clarity. In
other words, FIG. 15 shows the assembly of the tuned mass vibration
damper 300, also referred to as speed-adaptive damper, comprising
the variant of the damping component part 310 from FIG. 14. As can
be seen from the illustration, the damping component part 310 is
installed independently from the spacer rivets 180. Of course, the
rivets 180 can also be included in the geometry of the damping
component part 310 or can be taken into account in some other way.
For example, they can be located in the round cutouts of the
connection portions 440, possibly also in corresponding structures
of the damping portions 420. In so doing, the spacer rivets 180,
i.e., the spacer pieces or rivets, do not serve to radially support
the damping component part 310 or fix it in circumferential
direction. The damping component part 310 is also rotatably mounted
in this instance.
[0175] Embodiment examples of a tuned mass vibration damper 300 can
also include, for example, a plastic ring for supporting damper
masses 110, also referred to as flyweights, to improve acoustics. A
tuned mass vibration damper 300 of this kind can be implemented,
for example, as a speed-adaptive mass damper. The damping component
part 310 can serve, for example, as a driver element.
[0176] FIG. 16 shows a fragmentary front view of a further
embodiment example of a tuned mass vibration damper 300 according
to an embodiment example. For better clarity, the second guide
component part 130-2 is shown in section. The tuned mass vibration
damper 300 again has two guide component parts 130-1, 130-2 which
are also called left-hand path plate and right-hand path plate
because of the guide paths 170 which are implemented therein and
which are often plate-shaped. Here again, the tuned mass vibration
damper 300 has a damping component part 310, also referred to as
spacer ring. The two guide component parts 130-1, 130-2 are again
connected to one another by a plurality of spacer rivets 180, also
referred to as rivet or spacer pieces. Again, the tuned mass
vibration damper 300 has damper masses 110-1, 110-2, 110-3, 110-4,
also referred to as flyweights. The latter are guided in the
corresponding guide paths 170 of the guide component part 130 and
damper masses 110 by means of rolling bodies 210 which can be
constructed, for example, as stepped rollers 220.
[0177] FIG. 16 shows the assembly of the tuned mass vibration
damper 300 and components thereof with the damping component part
310 installed in neutral position in which the damper masses 110
occupy their center position.
[0178] Further, FIG. 16 shows the damping structures 350 and
damping portions 420 of the damping component part 310. In the
present case, the damping portions 420 are constructed as hollow
cylinders. The construction of the damping component part 310 will
be described in more detail referring to FIGS. 17a, 17b, 18a, 18b,
18c and 18d.
[0179] FIG. 17a shows a top view of the entire tuned mass vibration
damper 300 with installed damping component part 310. FIG. 17b
shows the tuned mass vibration damper 300 in a corresponding
sectional view along plane A-A shown as section plane in FIG. 17a.
In contrast to FIG. 16, the second guide component part 130-2 is
not shown in section in FIG. 17.
[0180] As is already shown by the partial arrangement of the
damping component 310 in front of damper masses 110-1 and 110-3 and
behind damper masses 110-2 and 110-4, this damping component part
310 has a plurality of circular-arc segment-shaped or
hollow-cylindrical segment-shaped circumferential portions 360-1,
360-2, 360-3 and 360-4. Accordingly, the number of circumferential
portions 360 precisely corresponds to the number of damper masses
110 in the embodiment shown here. Of course, this can be
implemented differently in other embodiment examples.
[0181] Circumferential portions 360-1 and 360-3 of support
structure 340 of damping component part 310 are located radially on
the second guide component part 130-2, while circumferential
portions 360-2 and 360-4 lie on the first guide component part
130-1. Here, the relevant circumferential portions are shaped
rather as ring segments in which an extension along the axis of
rotation 140 is shorter than a radial extension thereof.
[0182] The individual circumferential portions 360, which are also
arranged along the circumferential direction 160, corresponding to
their number, as adjacent circumferential portions, are connected
through four axial portions 450-1, 450-2, 450-3 and 450-4. Axial
portion 450-1 connects circumferential portions 360-1 and 360-2,
axial portion 450-2 connects circumferential portions 360-2 and
360-3, axial portion 450-3 connects circumferential portions 360-3
and 360-4, and axial portion 450-4 connects circumferential
portions 360-4 and 360-1. As suggested by their designation, the
axial portions extend substantially along the axial direction,
i.e., along the axis of rotation 140.
[0183] In the construction shown here, axial portions 450 extend in
a region between the damper masses 110. Therefore, they are
likewise used via corresponding connection portions 440 for
arranging or guiding the damping portions 420 which are shown in
cross section in the sectional view in FIG. 17b.
[0184] As can be seen in FIGS. 17a and 17b, for example, the
damping component part 310 is no longer shaped as an inner ring in
which the damping structures 350 extend radially outward, but
rather as an outer ring in which the relevant damping structures
350 extend radially inward. It can further be seen from FIGS. 17a
and 17b that the damping component part lies on the outer annular
surfaces of the two guide component parts 130-1, 130-2 and is
accordingly guided in circumferential direction 160 and likewise
held in radial direction by the guide component parts 130. The
damping component part 310 is held and guided axially along the
axis of rotation 140 between guide component parts 130 by damping
portions 420 of the damping structures 350.
[0185] FIGS. 18a, 18b, 18c and 18d show, respectively, a top view,
a side view, a sectional view of a section plane A-A shown in FIG.
18a, and a perspective view of the damping component part 310 of
the tuned mass vibration damper 300 from FIGS. 16, 17a and 17b. The
structure described with reference to FIGS. 17a and 17b is shown
again in FIGS. 18a to 18d.
[0186] These figures show much more clearly than FIGS. 17a and 17b
the arrangement of the circumferential portions 360 with the axial
portions 440 arranged therebetween and the connection portions 440
arranged at the latter and the damping portions 420 which are in
turn arranged at the latter. Damping portions 420 which, as was
already mentioned, are constructed as hollow cylinders have center
points which are arranged on a common pitch circle 460. These
damping portions 420 are connected to the support structure 340 via
connection portions 440, or more exactly, the circumferential
portions 360 thereof are connected via the connection portions 440
which have a smaller extension than an extension of the damping
portions 420 along the axis of rotation 140. In this way, it can be
possible optionally to prevent the connection portions 440 from
making contact with the guide component parts 130, not shown in
FIGS. 18a to 18d, to prevent line contact or point contact by
effects due to manufacture which may be brought about by edge radii
or the like, which could possibly lead to increased mechanical
loading of the damping component part 310.
[0187] Accordingly, the damping component part 310 is shown in four
views in FIGS. 18a to 18d. The damping component part 310 can again
be formed of a plastic, for example. Therefore, properties of the
damping component part 310 such as stiffness, strength, sliding
ability and other parameters can be influenced through the
selection of material.
[0188] With respect to function, a free oscillation angle of the
damper masses 110 is limited also in this embodiment example of a
tuned mass vibration damper 300 by means of the damping component
part 310, also referred to as ring element or spacer ring, which is
guided between the guide component parts 130 and/or outwardly of
guide component parts 130 of the tuned mass vibration damper 300.
Starting from an adjustable oscillating angle, the damping
structures 350 located between the damper masses 110, i.e., the
portions of the damping component part 310 located between the
damper masses 110, are possibly compressed and, therefore,
elastically deformed so that a deflection of the damper masses 110
beyond the adjusted angle is damped. During operation or after the
engine is switched off as well as in crawl operation of the
vehicle, this can result in a damping of the damper masses 110 in
the stops thereof or in the ends 230 of the guide paths 170.
[0189] Due to the rotatable supporting of the damping component
part 310, the free oscillation of the damper masses 110 in the
defined angle is hardly impaired or possibly entirely unimpaired.
Further, the damper masses 110 can be supported relative to one
another by spring rings when dropping down and can therefore be
held so as to be spaced apart so that they can be prevented from
colliding with one another, which could occur, for example, when
the engine is switched off. Accordingly, a rattling noise which may
be perceptible in the vehicle as well as outside of the vehicle in
a conventional solution can be reduced or eliminated to the extent
that it is no longer perceptible. Accordingly, a functionality of
the damper masses 110 can be maintained unimpeded in that the
damping component part 310 is rotatable and a rigid coupling is not
implemented between the damper masses 110. Therefore, every damper
mass 110 works alone or by itself precisely because the damper
masses 110 are not coupled with one another.
[0190] FIG. 19 shows a view of the tuned mass vibration damper 300
which is comparable to FIG. 16 but in which the second guide
component part 130-2 is not shown for the sake of better clarity.
Apart from this, FIGS. 16 and 19 differ in that the damper masses
110 in FIG. 16 are arranged substantially in their center position,
whereas in the situation depicted in FIG. 19 they are located in
the region of their path ends 230, i.e., in the region of the
maximum torsional angle or oscillating angle.
[0191] FIG. 19 shows the tuned mass vibration damper 300 with
damper masses 110 deflected to the maximum extent. Before the
damper masses 110 can reach their stops or ends 230 of their guide
paths 170, also referred to as oscillating paths, an elastic
deformation (compression) is carried out at the portions located
between the damper masses 110, i.e., inter alia at the damping
portions 420 of the damping component part 310. These damping
portions 420 are also referred to as compression bodies. In this
way, an impact of the damper masses 110 against the respective path
ends 230 is damped. In this connection, the damping component part
310 executes a comparatively small amplitude.
[0192] More precisely, FIG. 19 shows the situation during engine
operation. The free oscillation angle of the damper masses 110,
which is given in the present embodiment example precisely by the
fact that no significant compression or elastic deformation is
achieved at the damping structures 350 through the damper masses
110, as well as the maximum torsional angle (maximum oscillation
angle) of the damping component part 310 can be adapted as needed
via a change in the geometry of the damper masses 110 and damping
structures 350, for example, by adapting the damping portions 420.
Accordingly, it may be advisable to adapt the shape of the damper
masses 110 to a shape of the damping structures 350 or damping
portions 420 in an area in which the damper masses 110 make contact
with the damping structure 350.
[0193] It can be possible in this way to eliminate the
above-described collision of damper masses 110 with one another
during operation so that greater masses of the damper masses 110,
i.e., a greater mass of the flyweights, can possibly be
realized.
[0194] As was already mentioned, the conditions are different in a
further state in which the engine is switched off, or has already
been switched off, but the transmission input shaft continues to
run, or in a crawl operation of the engine. During slow crawling,
the transmission input shaft rotates at a lower rate of rotation
than the engine. In this state, the weight force 250 of the damper
masses 110 is appreciably higher than the opposed component of
centrifugal force 240. The situation is similar when switching off
the engine. The transmission input shaft continues to run for
several seconds. After a determined time, the weight force exceeds
the opposed centrifugal force component, and the damper masses 110
can drop in an uncontrolled manner in both of the states described
above.
[0195] FIGS. 20a and 20b show a view of the tuned mass vibration
damper 300 in two different operating situations. For simplicity,
the second guide component part 130-2 is not shown again.
[0196] FIG. 20a shows a situation corresponding to the operation of
the motor vehicle. In operation, the damper masses 110 are pressed
radially outward due to the comparatively high centrifugal forces
240 and correspondingly move along their guide paths 170. The
movement of the damper masses 110 is essentially predetermined by
the geometry of the guide paths 170 in the damper masses 110 and in
the relevant guide component parts 130.
[0197] However, during a crawl operation of the vehicle or when the
engine is switched off, the centrifugal force 240 may no longer be
sufficient to keep the damper masses 110 in their nominal
positions. Depending on the angular position of the tuned mass
vibration damper 300, they either fall down or slide along the
guide paths 170. The damping component part 310, also referred to
as spacer ring, prevents the nominal movement of the damper masses
110 in the guide paths 170 in that they are supported relative to
one another as is shown in FIG. 20b. This prevents the damper
masses 110 from dropping into their path ends 230 or at least
softens the fall to the extent that the rattling noise described
above no longer occurs or at least not to the same extent. In other
words, it can be possible in this way to prevent the rattling
noise.
[0198] FIGS. 21a, 21b, 21c and 21d show a further possible variant
of a damping component part 310 in which a radial support of the
damping component part 310 on the guide component parts 130 is not
implemented. FIG. 21a shows a top view of the damping component
part 310, FIG. 21b shows a side view of the damping component part
310, FIG. 21c shows a sectional view of the damping component part
310 along the section plane A-A shown in FIG. 21a, and FIG. 21d
shows a perspective view of the damping component part 310.
[0199] The damping component part 310 from FIG. 21 differs from
that in FIG. 18 is several aspects. Specifically, the support
structure 340 is now formed as a hollow cylinder so that the
support structure 340 also has only one circumferential portion
360. Accordingly, the axial portions 450 which connected the
individual circumferential portions 360 in FIG. 18 are dispensed
with.
[0200] In this case, the damping portions 420 are again shaped as
hollow cylinders which are in turn connected via corresponding
connection portions 440 to the support structure 340. However, in
this case the connection portions 440 extend appreciably farther
radially inward than in the damping component part 310 in FIG. 18.
Correspondingly, the center points of the damping portions 410 are
arranged on a smaller pitch circle 460. The connection portions 440
are web-shaped in this case and extend substantially radially
inward proceeding from the support structure 340.
[0201] In this embodiment, the damping portions 420 (compression
bodies) of the damping component part 310 are located between the
guide component parts 130 of the tuned mass vibration damper 300 so
that the damping component part 310 is fixed in axial direction.
However, the damping component part 310 is freely movable radially
and is supported only via the support structure 340 and damping
structures 350 on the damper masses 110. Accordingly, when the
damper masses 110 drop down the damping component part can move
along with them in direction of gravity force. In this way, it can
be possible optionally to further reduce an influence of the
damping component part 310 on the functioning of the damper masses
110 and accordingly to have less of a negative effect, or none at
all, on the performance of the tuned mass vibration damper 300.
[0202] Further exemplary constructions of a damping component part
310 in which the damping component part 310 is supported in radial
direction only on one of the guide component parts 130 are shown in
the following FIGS. 22, 23 and 24 and the parts thereof. This
configuration can make it possible optionally to carry out the
damping component part 310 in a tuned mass vibration damper 300
(speed-adaptive damper) also with a slight spacing between the
damper masses 110 and other component parts on a side of the damper
masses 110 along the axis of rotation 140.
[0203] FIGS. 22a, 22b and 22c show a further damping component part
310 in a top view, cross-sectional view along a section plane A-A
shown in FIG. 22a, and in a perspective view. In this case again,
the support structure 340 is configured in such a way that it has
only one single circumferential portion 360 which completely
surrounds the axis of rotation 140 and is ring-shaped, i.e., has an
extension along the axis of rotation 140 which is smaller than a
corresponding extension in radial direction. In contrast, a
hollow-cylindrical shape has an extension along the axis of
rotation 140 which has at least an extension of the hollow cylinder
within the meaning of a difference between an outer radius of the
hollow cylinder and an inner radius of a hollow cylinder along the
radial direction.
[0204] In the present embodiment of the damping component part 310,
the connection structures 440 are arranged along the axis of
rotation 140 and guide the damping portions 420 on the pitch circle
460 radially inward toward the axis of rotation 140. In this way,
it is possible to use the support structure for radial guiding at
one of the guide component parts 130 (not shown in FIG. 22). Here
also, the damping portions 420 are hollow-cylindrical.
[0205] FIGS. 23a, 23b, 23c and 23d again show a further damping
component part 310 in a top view, a side view, a cross-sectional
view along the section plane A-A shown in FIG. 23a, and in a
perspective view. This damping component part 310 differs from the
damping component part 310 shown in FIG. 22 essentially with
respect to the construction of the support structure 340. This
support structure 340 has four circumferential portions 360-1,
360-2, 360-3, 360-4, each of which is ring segment-shaped and
connected to one another via the damping structures 350. The
circumferential portions 360 substantially lie in a plane such as
is shown by way of example in FIGS. 23b and 23c so that no axial
portions 450 are implemented here either.
[0206] More precisely, the damping structures 350 in this case
again have hollow-cylindrical or hollow-cylindrical segment-shaped
damping portions 420 which are mechanically coupled to two adjacent
circumferential portions 360, for example, circumferential portions
360-1 and 360-4, by means of two connection portions 440-1, 440-2,
respectively. In this way, it can be possible optionally to also
implement a determined spring effect along the circumferential
direction 160. Here again, the damping component part is guided
radially through a guide component part 130, not shown in FIG.
23.
[0207] FIGS. 24a, 24b, 24c and 24d show, respectively, a further
damping component part 310 in a top view, a side view, a sectional
view along a section plane A-A shown in FIG. 24a, and a perspective
view. This damping component part 310 differs from the damping
component part 310 shown in FIG. 23 essentially in that, instead of
the two separate connection portions 440-1, 440-2, a U-shaped
connection portion 440 is used which, in addition to two legs
extending in axial direction, also has a portion extending along
the circumferential direction 160. By means of this U-shaped
connection portion 440, the damping portions 420 of the damping
structures 350 are arranged on the pitch circle 460 and
respectively connect two adjacently arranged circumferential
portions 360, for example, circumferential portions 360-1,
360-4.
[0208] FIGS. 25a, 25b, 25c and 25d show a further damping component
part 310 in a top view, a side view, a sectional view along a
section plane A-A shown in FIG. 25a, and a perspective view. This
damping component part 310 differs from the damping component part
310 shown in FIG. 24 in that it has a guide structure 380 at a side
remote of the support structure 340 along the axis of rotation 140,
this guide structure 380 being implemented in the form of a
projection 390. As a result of the guide structure 380, the damping
component part 310 is no longer supported at only one guide
component part 130, but can now be supported at two guide component
parts 130-1, 130-2 (not shown in FIG. 25). In other words, the
drawing parts in FIG. 25 show a further variant of the damping
component part 310 in which the latter can be supported in radial
direction on both guide component parts 130.
[0209] It should be mentioned again here purely for the sake of
completeness that the damping portions 420 can, of course, also be
constructed from solid material instead of as a hollow body as has
been the case in the description thus far. Not only can the
hollow-cylindrical or hollow-cylindrical segment-shaped
configurations be selected, but also diverse variations with
respect to geometry and composition can be selected. Some of these
variations are shown by way of example in FIGS. 26a to 26d.
[0210] FIGS. 26a to 26d show, respectively, a detail of a damping
component part 310 with a damping structure 350 and a damping
portion 420 which are directly or indirectly connected to the
support structure 340. In the case of the damping component part
310 from FIG. 26a, the damping portion 420 is web-shaped and
extends substantially along the radial direction. It has at both
sides along the circumferential direction 160 a coating 470 of the
surfaces of the damping portion 420. This coating 470, also
referred to as damping layer, can be made of different materials,
for example, rubber or another elastomer, to mention only one
example. The coating can be applied to the damping portion 420 by
means of different techniques. It may also be possible to apply the
relevant coating not only in the area of the damping portion 420
which can make contact with the damper masses 110, but, on the
contrary, it is also possible and perhaps advisable, as the case
may be, to coat the entire damping component part 310, for example,
to realize desired properties of stiffness, strength, sliding
properties or other functional characteristics.
[0211] FIG. 26b shows a further embodiment of a damping structure
350 in which the damping portion 420 is substantially U-shaped and
in which only one leg of the damping portion 420 is connected to
the support structure 340 via a connection portion 440.
[0212] On the other hand, FIG. 26c shows a further embodiment in
which the damping structure 350 and damping portion 420 are formed
by a hollow box-shaped portion with an outer contour in the shape
of a polygon or rectangle extending in a plane perpendicular to the
axis of rotation 140.
[0213] Finally, FIG. 26d shows an embodiment of a damping structure
350 in which the damping portion 420 is cross-shaped and is
likewise connected to the support structure 340 via a connection
portion 440.
[0214] FIGS. 27a to 27d and 28a to 28c show a further variant of a
damping component 310 and a corresponding tuned mass vibration
damper 300 according to an embodiment example. This variant is a
damping component 310 with only two damping portions 420 located
opposite each other. When using a variant of this type, it may be
advisable to install two damping components 310 within a tuned mass
vibration damper 300 as is indicated in FIGS. 28a to 28c. The two
damping component parts 310, which can possibly be identically
constructed, can be installed at a 90-degree rotation with respect
to one another. FIGS. 27a, 27b, 27c and 27d show a top view, a side
view, a sectional view along the section planes A-A shown in FIG.
27a, and a perspective view through the damping component part 310
which very closely resembles the damping component part 310 shown
in FIGS. 24a to 24d. It differs from the damping component part 310
shown in FIG. 24 essentially in that, instead of four damping
structures 350, the damping component part 310 now has only two
damping structures 350 located opposite one another, i.e., arranged
at an offset of 180.degree. with respect to one another. These
damping structures 350 are substantially identical to those in FIG.
24. Only the connection portions 440 have an additional small
recess 480 at a radially inwardly located area which can be
implemented, for example, to reduce weight, but also to adapt to a
mechanical characteristic of the relevant damping component part
310.
[0215] FIGS. 28a and 28b show the overall assembly of the tuned
mass vibration damper 300 according to an embodiment example in a
sectional view and in an isometric or perspective view in which the
second guide component part 130-2 is again omitted for better
clarity. The constructional configuration of the tuned mass
vibration damper 300 corresponds substantially to that of the tuned
mass vibration damper 300 shown in FIGS. 16, 17a and 17b. However,
the two tuned mass vibration dampers differ in that different
damping component parts 310 are used. Whereas one individual
damping component part 310 was used in the arrangement shown in
FIGS. 16, 17a and 17b, two damping component parts 310-1, 310-2 are
used in this case and are integrated so as to be turned
substantially by 90.degree. relative to one another at opposite
sides along the axis of rotation 140 at ends of the tuned mass
vibration damper 300. The first damping component part 310-1 has
the two damping structures 350-1 and 350-2, while the second
damping component part 310-2 has the two damping structures 350-3
and 350-4. FIG. 28c shows the orientation of the two damping
component parts 310-1, 310-2 relative to one another without the
further components of the tuned mass vibration damper 300.
[0216] Accordingly, this tuned mass vibration damper 300 comprises
at least four damper masses 110 and at least two damping component
parts 310. The damping component parts 310 are arranged and
configured precisely in such a way that each of the damper masses
110 can make contact with a damping structure 350 of a different
damping component part 310 during a movement along a first
direction along the circumferential direction 160 than during a
movement along a second direction opposite to the first
direction.
[0217] More precisely, the two damping component parts are arranged
precisely in such a way that a first damping structure of the
second damping component part 310 is arranged between the first
damper mass 110-1 and the second damper mass 110-2 arranged
adjacent to the latter. A second damping structure 350-4 of the
second damping component part 310-2 is likewise arranged between
the third damper mass 110-3 and the fourth damper mass 110-4
arranged adjacent to the latter. Also, the first damping structure
350-1 of the first damping component part is arranged between the
fourth damper mass 110-4 and the first damper mass 110-1 arranged
adjacent to the latter.
[0218] This also applies to the second damping structure 350-2 of
this damping component part 350-1 which is arranged between the
second damper mass 110-2 and the third damper mass 110-3 arranged
adjacent to the latter. The damping structures 350 are all formed
and arranged precisely in such a way that the relevant damper
masses 110 between which they are arranged can make contact with
them in order to prevent the two adjacent damper masses 110 from
touching one another in the manner described above.
[0219] In this case also, damping component parts 310 can be used,
for example, as ring elements to improve acoustics in
speed-adaptive dampers such as can be used, for example, in
hydrodynamic converters or other start-up elements.
[0220] The embodiment examples and individual features thereof
disclosed in the preceding description, appended claims and
accompanying drawings can be significant and can be implemented
individually as well as in any combination for realizing an
embodiment example in its various refinements.
* * * * *