SE1451045A1 - A vibration absorbing device for reducing vibrations and sounds in a structure - Google Patents
A vibration absorbing device for reducing vibrations and sounds in a structure Download PDFInfo
- Publication number
- SE1451045A1 SE1451045A1 SE1451045A SE1451045A SE1451045A1 SE 1451045 A1 SE1451045 A1 SE 1451045A1 SE 1451045 A SE1451045 A SE 1451045A SE 1451045 A SE1451045 A SE 1451045A SE 1451045 A1 SE1451045 A1 SE 1451045A1
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- Prior art keywords
- dynamic element
- absorbing device
- vibration absorbing
- axis
- vibration
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F7/00—Vibration-dampers; Shock-absorbers
- F16F7/10—Vibration-dampers; Shock-absorbers using inertia effect
- F16F7/104—Vibration-dampers; Shock-absorbers using inertia effect the inertia member being resiliently mounted
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
- F16F15/02—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems
- F16F15/04—Suppression of vibrations of non-rotating, e.g. reciprocating systems; Suppression of vibrations of rotating systems by use of members not moving with the rotating systems using elastic means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2222/00—Special physical effects, e.g. nature of damping effects
- F16F2222/08—Inertia
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Vibration Prevention Devices (AREA)
Description
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ln various aircraft contexts, for instance propeller-driven aircraft,
two or several motor speeds are typically used during flight to
optimize performance, fuel consumption or comfort at various
flight states. These various motor speeds result in vibrations
and sounds with two or several relatively well defined
fundamental frequencies. The known passive vibration
absorbing devices only give the desired reduction of vibrations
and sounds at one of the motor speeds and related frequency.
At the other motor speeds the influence of a passive vibration
absorbing device may be an increase of the vibrations and
sounds.
This problem has been addressed in WO 2006/083223 showing
a vibration absorbing device, which thanks to the rotatable
spring element will be adaptive. The spring element will adjust
itself to such a rotary position that a maximum vibration
amplitude is achieved for the oscillating mass of the spring
element at vibration excitation at, or in the proximity of, one of
the resonance frequencies of the device. The known device may
thus, without any actuating members, absorb two different
vibration frequencies. WO 2006/083222 shows another similar
adaptive vibration absorbing device.
SUMMARY OF THE INVENTION
One problem which could occur with the known vibration
absorbing devices is that the dynamic element may be in a
disadvantageous position when a vibration is excited in the
structure. Such a disadvantageous position is when the vibration
direction of the vibration in the structure is perpendicular to the
desired oscillation direction of the dynamic element for a
specific frequency. Thus, the dynamic element may be
prevented from rotating to the one of the first rotary position and
the second rotary position in which the oscillation direction is
parallel with the vibration direction, or the adaptation will be so
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slow that the function of the vibration absorbing device is
significantly reduced.
This problem is solved by the device initially defined, which is
characterized in that the device comprises a positioning
mechanism configured to position the dynamic element in a
neutral rotary position, different from the first rotary position and
the second rotary position, when the structure does not vibrate.
Such a positioning mechanism will thus prevent the dynamic
element from reaching a rotary position in which its desired
oscillation direction is perpendicular to the vibration direction of
the excited vibration of the structure.
lt is to be noted that the vibration direction of the vibration of the
structure is normally known. The positioning mechanism may
thus be easily adjusted to a preferred neutral rotary position in a
non-vibrating state of the structure when mounting the vibration
absorbing device to the structure.
The dynamic element will adjust itself from the neutral rotary
position to one of the first rotary position and the second rotary
position so that a maximum vibration amplitude is achieved for
the oscillating mass of the dynamic element at vibration
excitation at, or in the proximity of, one of the resonance
frequencies of the vibration absorbing device.
ln some cases, for example when the vibration amplitude is very
low, the adjusting may be slow. Energy absorption is however,
acquired also for intermediate rotary positions between the first
rotary position and the second rotary position.
The positioning mechanism may be designed to have a very
specific relation between the rotation relative to the neutral
rotary position and the moment (torque) given by the positioning
mechanism. Such specific relations between rotary position of
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the dynamic element and the moment may thus include a
progressive behavior with a low moment for low rotation and a
significant increase of the moment at a certain rotation.
According to an embodiment of the invention, the dynamic
element comprises an elastic element extending along the axis
of rotation.
The oscillation of the elastic element may be obtained through
an energy-absorbing bending of the elastic element.
Alternatively, or supplementary, the oscillation of the elastic
element may be obtained through an energy-absorbing shearing
of the elastic element.
According to a further embodiment of the invention, the elastic
element provides said different rigidity of the dynamic element.
According to a further embodiment of the invention, the dynamic
element has a mass element provided on the elastic element
and forming a dynamic mass.
According to a further embodiment of the invention, the mass
element provides said different rigidity.
The different rigidity of the dynamic element may be obtained
through a geometric design of the dynamic element, i.e. the
elastic element or the mass element, with a different geometric
shape along the two main axes, e.g. the dimension along the
first main axis may be different from the dimension along the
second main axis. The different rigidity of the dynamic element
may also be obtained through an orthotropic material of the
dynamic element, i.e. the elastic element or the mass element.
According to a further embodiment of the invention, the elastic
element comprises an intermediate segment, a first outer
segment and a second outer segment, which extend along the
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axis of rotation and are rotatable in relation to each other and
the attachment. Advantageously, the intermediate segment, the
first outer segment and the second outer segment may provide
said different rigidity. By such an elastic element, the vibration
absorbing device may adapt itself to possibly eight different
angular resonance frequencies.
According to a further embodiment of the invention, the first
outer segment and the second outer segment are mechanically
coupled to each outer. With such a coupling, a symmetric elastic
element is obtained, which may adapt itself to four different
angular resonance frequencies.
According to a further embodiment of the invention, the vibration
absorbing device comprises two rotary bearings, which are
mounted to the attachment and thus are mechanically connected
to the structure, wherein the dynamic element at a respective
end thereof is journalled in the two rotary bearings to be
rotatable around the axis of rotation.
With such a double support of the dynamic element, two elastic
elements are formed, one on each side of the mass element or
on each side of a central position of the dynamic element, which
elastic elements will act as a combined spring and thus reduce
the required accuracy of the mounting of the dynamic element.
This will allow for proper functioning of the vibration absorbing
device even if there is a small difference in properties for the
two elastic elements.
Advantageously, at least one of the rotary bearings comprises a
pin bearing.
According to a further embodiment of the invention, the
positioning mechanism comprises a weight provided on the
dynamic element to rotate the dynamic element to the neutral
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rotary position by means of the gravity force when the structure
does not vibrate.
According to a first variant of this embodiment, the weight is
attached to the elastic element.
According to a second variant of this embodiment, the weight is
attached to the mass element.
According to a further embodiment of the invention, the
positioning mechanism comprises a spring arrangement acting
on the dynamic element to rotate the dynamic element to the
neutral rotary position when the structure does not vibrate.
Advantageously, the spring arrangement may comprise at least
one spring connected to the dynamic element.
According to a first variant of this embodiment, the at least one
spring is attached to the elastic element.
According to a second variant of this embodiment, the at least
one spring is attached to the mass element.
According to a further embodiment of the invention, the at least
one spring comprises a spring having a non-linear characteristic
and a progressive behavior with a low moment for low rotation of
the dynamic element and a significantly higher moment at a
certain rotation of the dynamic element.
With such a non-linear spring, the spring arrangement may thus
be designed to have the very specific relation between the
rotation relative to the neutral rotary position and the moment
(torque) given by the spring arrangement.
According to a further embodiment of the invention, the
positioning mechanism comprises a magnet arrangement acting
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on the dynamic element to rotate the dynamic element to the
neutral rotary position when the structure does not vibrate.
Advantageously, the magnet arrangement comprises a first
magnet connected to the dynamic element and a second magnet
connected to the attachment.
According to a second variant of this embodiment, the first
magnet is attached to the mass element.
According to a first variant of this embodiment, the first magnet
is attached to the elastic element.
BRIEF DESCRIPTION OF THE DRAWINGS
The present invention is now to be explained more closely
through a description of various embodiments and with
reference to the drawings attached hereto.
Fig1 discloses schematically a side view of a vibration
absorbing device according a first embodiment of the
present invention.
discloses schematically a cross-section through the
vibration absorbing device in a first rotary position.
discloses schematically a cross-section through the
vibration absorbing device in a second rotary
position.
discloses schematically a cross-section through the
vibration absorbing device in a neutral rotary
position.
discloses schematically a cross-section through the
vibration absorbing device according to a second
embodiment of the present invention.
discloses schematically a cross-section through the
vibration absorbing device according to a third
embodiment of the present invention.
Fig 2
Fig 3
Fig 4
Fig 5
Fig 6
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Fig 7 discloses schematically a cross-section through the
vibration absorbing device according to a fourth
embodiment of the present invention.
discloses schematically a cross-section through the
vibration absorbing device according to a fifth
embodiment of the present invention.
discloses schematically a side view of a vibration
absorbing device according to a sixth embodiment of
theinvenüon.
discloses schematically a side view of a vibration
absorbing device according to a seventh embodiment
of the invention.
discloses schematically a side view of a vibration
absorbing device according to a eight embodiment of
theinvenüon.
Fig 8
Fig 9
Fig 10
Fig 11
DETAILED DESCRIPTION OF VARIOUS EMBODIMENTS
Fig 1 discloses a first embodiment of a vibration absorbing
device for reducing vibrations and sounds in a structure 1. The
structure 1 may be a vehicle, for instance an aircraft, a car, or a
ship, or any stationary structure, for instance a building, a
machine tool or any other stationary installation, where it is
desirable to reduce sounds or vibrations.
The vibration absorbing device comprises an attachment 2,
which is configured to be attached to the structure 1 in any
suitable manner, for instance by means of one or more screw
joints 3, schematically indicated.
Furthermore, the vibration absorbing device comprises a
dynamic element 4. The dynamic element 4 has two opposite
ends. ln the first embodiment, the two ends are supported by
and journalled in a respective one of two rotary bearings 5 to be
rotatable around an axis x of rotation. The dynamic element 4 is
at least partly elastic and has a spring constant k.
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The two rotary bearings 5 are mounted to the attachment 2. The
rotary bearings 5 are thus mechanically connected to the
structure 1. One, or possibly both, of the two rotary bearings 5
comprises a pin bearing.
ln the first embodiment, the dynamic element 4 comprises an
elastic element 6 extending along the axis x of rotation. The
elastic rod 6 may be made of any suitable elastic material, for
instance spring steel, composite material, etc., to provide elastic
properties with said spring constant k permitting the elastic rod
6 to flex and oscillate. ln the embodiments disclosed, the elastic
element 6 is in the form of an elastic rod.
The oscillation of the elastic element 6 may be obtained through
an energy-absorbing bending of the elastic element 6.
Alternatively, or supplementary, the oscillation of the elastic
element 6 may be obtained through an energy-absorbing
shearing of the elastic element 6. ln this case, the elastic
element 6, may have a smaller longitudinal extension along the
axis x of rotation than in the embodiments disclosed.
As has been indicated in Fig 1, the two ends held by the rotary
bearings 5 are comprised by the elastic element 6.
ln the first embodiment, the dynamic element 4 also comprises a
mass element 7 provided on the elastic element 6 at a central
position of the elastic element 6. The mass element 7 forms a
dynamic mass of the dynamic element 4.
lt should be noted that it is possible to dispense with the mass
element 7. The dynamic mass of the dynamic element 4 may
then be provided by the elastic element 6.
The dynamic element 4 has at least partly a cross-section, see
Fig 2, which defines a first main axis y, perpendicular to the axis
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x of rotation, and a second main axis z, perpendicular to the first
main axis y and to the axis x of rotation. The dynamic element 4
has a different rigidity with respect to the first main axis y and
the second main axis z.
ln the first embodiment, the elastic element 6 provides the
different rigidity of the dynamic element 4 along the first main
axis y and the second main axis z. Fig 2 discloses a cross-
section through the elastic element 6.
The different rigidity of the dynamic element 4 may be obtained
through a geometric design of the dynamic element 4, i.e. the
elastic element 6 and/or the mass element 7. ln Figs 2 and 3,
the cross-sectional dimension of the elastic element 6 is longer
along the first main axis y than along the second main axis z.
The different rigidity of the dynamic element 4 may also be
obtained through an orthotropic material of the dynamic element
4, i.e. the elastic element 6 and/or the mass element 7.
ln case of a vibration in the structure 1, the dynamic element 4
is brought to take a first rotary position, in which the dynamic
element 4 will oscillate along the first main axis y, or a second
rotary position, in which the dynamic element 4 will oscillate
along the second main axis z.
ln Fig 2, the dynamic element 4 is adjusted to the first rotary
position, in which the first main axis y is parallel to the vibration
direction v. The structure 1 then vibrates with an angular
resonance frequency wy = (ky/m)'/2 of the vibration absorbing
device, wherein ky corresponds to the spring constant of the
dynamic element 4 with respect to the first main axis y and m is
the effective modal mass. The dynamic element 4 will oscillate
in the direction of the first main axis y.
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ln Fig 3, the dynamic element 4 is rotated 90° and has thus
adjusted itself to the second rotary direction in which the second
main axis z is parallel to the vibration direction v. The structure
1 then vibrates with an angular resonance frequency wz =
(kZ/m)1/2 of the vibration absorbing device, wherein kz
corresponds to the spring constant of the dynamic element 4
with respect to the second main axis z. The dynamic element 4
will oscillate in the direction of the second main axis z.
lf the structure 1 vibrates with the angular frequency wz and the
dynamic element 4 is in the first rotary position, the dynamic
element 4 may not rotate to the second rotary position in which
the oscillation direction is parallel with the vibration direction v.
ln the same way, if the structure 1 vibrates with the angular
frequency wy and the dynamic element 4 is in the second rotary
position, the dynamic element 4 may not rotate to the first rotary
position in which the oscillation direction is parallel with the
vibration direction v.
ln order to prevent the dynamic element 4 from being locked in
such a disadvantageous position, the vibration absorbing device
comprises a positioning mechanism configured to position the
dynamic element 4 in a neutral rotary position, different from the
first rotary position and the second rotary position, when the
structure 1 does not vibrate.
Consequently, in case of a vibration in the structure 1, the
dynamic element 4 is brought to take the first rotary position, in
which the dynamic element 4 will oscillate along the first main
axis y, or the second rotary position, in which the dynamic
element 4 will oscillate along the second main axis z, if the
frequency of the vibration is such that it matches one of the
angular resonance frequencies wz, wy of the vibration absorbing
device.
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The vibration absorbing device is thus self-adaptable to achieve
maximum vibrations absorption of two different vibration
frequencies.
According to the first embodiment, the positioning mechanism
comprises a weight 11 provided on the dynamic element 4. The
weight 11 will rotate the dynamic element 4 to the neutral rotary
position, see Fig 4, by means of the gravity force when the
structure 1 does not vibrate. The weight 11 is attached to the
mass element 7 as can be seen in Figs 2-4.
lt should be noted, that the weight 11 alternatively could be
attached to the elastic element 6.
According to a second embodiment, the positioning mechanism
comprises a spring arrangement acting on the dynamic element
4 to rotate the dynamic element 4 to the neutral rotary position
when the structure 1 does not vibrate, see Fig 5. ln the second
embodiment, the spring arrangement comprise two springs 12,
which are connected to the dynamic element 4. The two springs
12 are attached to the mass element 7 at a respective first end
and are attached to the attachment 2 at a respective second
end.
Fig 6 discloses a third embodiment, which differs from the fourth
embodiment in that the spring arrangement comprises only one
spring 12 holding the dynamic element 4 in the neutral rotary
position. The springs 12 is attached to the mass element 7 at a
first end and to the attachment 2 at a second end.
lt should be noted, that the springs 12, or said one spring 12,
instead of being attached to the mass element 7, alternatively,
could be attached to the elastic element 6.
The spring or springs 13 may have a non-linear characteristic. ln
particular, the spring or springs 13 may have a progressive
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13
behavior with a low moment (torque) for low rotation of the
dynamic element 4 and a significantly higher moment (torque) at
a certain higher rotation of the dynamic element 4.
According to a fourth embodiment, the positioning mechanism
comprises a magnet arrangement 14 acting on the dynamic
element 4 to rotate the dynamic element 4 to the neutral rotary
position, see Fig 7, when the structure 1 does not vibrate. The
magnet arrangement 14 comprises a first magnet 15 attached to
the mass element 7 and two second magnets 16 attached to the
attachment 2. The first and second magnets 15 and 16 have the
same polarity, positive or negative, i.e. they are repelling each
other.
Fig 8 discloses a fifth embodiment, which differs from the fourth
embodiment in that the second magnets 16 have been replaced
by one magnet 17. ln this embodiment, the first magnet 15 and
the second magnet 17 have different polarity, i.e. they are
attracting each other.
The sounds and vibrations may emanate directly from an
engine, transmission or the like of a vehicle or a stationary
installation. However, the vibration absorbing device may also
be used to alter and reduce the peak of a resonance in the
structure 1, for instance squeal from brakes. This as a result of
the inherent energy absorption capability for the two angular
resonance frequencies my and coz.
Excitation of both the two angular resonance frequencies toy and
m2 of the vibration absorbing device will result unless the rotary
position is such that the vibration direction is exactly in one of
the main axes.
The positioning mechanism assures that the vibration absorbing
device is forced towards the neutral rotary position when no
vibrations are present. The neutral rotary position can be
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14
selected for each specific structure in order to adapt for specific
structural resonances and specific excitation frequencies. For
example the neutral position me be selected to improve the
adaptation to a frequency of vibration that normally is first in an
operating cycle like a flight envelope. Similarly the neutral
position may be selected to improve the adaptation to reduce
the statistically most likely resonance while the adaptation to
less likely resonances thus becomes slower.
Fig 9 discloses a sixth embodiment, which differs from the
previous embodiments in that the dynamic element 4 is
supported by one rotary bearing 5 only. ln a first variant, the
rotary bearing 5 engages one end of the dynamic element 4, i.e.
the elastic element 6, whereas the other end of the dynamic
element 4 is free. A mass element 6 may be provided at the
other free end of the elastic element 6.
ln a second variant, not disclosed, the rotary bearing 5 engages
the dynamic element 4, i.e. the elastic element 6, at a central
position thereof, wherein both ends of the dynamic element 4
are free. A mass elements 7 may be provided at a respective
one of the free ends of the elastic element 6.
These variants are explained more closely in WO 2006/083223
discussed above, which is incorporated herein by reference.
Fig 10 discloses a seventh embodiment, which differs from the
previous embodiments in that the elastic element 6 comprises
three elastic segments, namely an intermediate segment 6a, a
first outer segment 6b and a second outer segment 6c, which
extend along the axis x of rotation and are rotatable in relation
to each other and the attachment 2. The intermediate segment
6a is connected to the first outer segment 6b by means of a
rotary bearing 5b and to the second outer segment 6b by means
of a rotary bearing 5b. All of the segments 6a-6b provides the
different rigidity as the elastic element 6 of the previous
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embodiments. The independently rotatable segments 6a-6c may
permit the vibration absorbing device to adapt itself to possibly
eight different angular resonance frequencies.
ln the seventh embodiment, the intermediate segment 6a is
provided with a mass element 7. A positioning mechanism
comprising a weight 11 is provided on the intermediate segment
6a. Also the positioning mechanisms discussed above in the
second to fifth embodiments may be employed. lt is also to be
noted that also the first and second outer segments 6b, 6c may,
but do not have to, comprise a positioning mechanism as
indicated in Fig 10.
Fig 11 discloses an eight embodiment, which differs from the
seventh embodiment in that the first outer segment 6b and the
second outer segment 6c are coupled to each outer by means of
a suitable mechanical element 18, schematically indicated as a
dashed line. Thanks to the mechanical element 18, symmetry is
achieved. The first outer segment 6b and the second outer
segment 6c will act as one elastic element, which, together with
the intermediate segment 6a, permits the vibration absorbing
device to adapt itself to four different angular resonance
frequencies.
lt should be understood, the dynamic element 4 may comprise
another number of elastic elements than disclosed above in
order to create symmetry and/or to permit the vibration
absorbing device to adapt itself to several different angular
frequencies.
The present invention is not limited to the embodiments
disclosed but may be varied or modified within the scope of the
following claims.
16
lt should be noted that the progressive behavior mentioned
above may also be achieved with a positioning mechanism
comprising the magnet arrangement 14, or the weight 11.
Claims (15)
1. En vibrationsabsorptionsanordning för reducering av vibrat- ioner och ljud i en struktur (1), innefattande ett fäste (2), som är utformat att fästas på strukturen (1), åtminstone ett rotationslager (5), som är monterat på fästet (2) och således mekaniskt förbundet med strukturen (1), och ett dynamiskt element (4) lagrat i rotationslagret (5) för att vara roterbart runt en rotationsaxel (x), varvid det dynamiska elementet (4) är åtminstone delvis elastiskt, varvid det dynamiska elementet (4) åtminstone delvis har ett tvär- snitt, som definierar en första huvudaxel (y), som är vinkelrät mot rotationsaxeln (x), och en andra huvudaxel (z), som är vinkelrät mot den första huvudaxeln (y) och mot rotationsaxeln (x), varvid det dynamiska elementet (4) har olika rörelsemotstånd med av- seende på den första huvudaxeln (y) och den andra huvudaxeln (z), och varvid en vibration i en vibrationsriktning (v) i strukturen (1) kom- mer att bringa det dynamiska elementet (4) till att inta en första rotationsposition, i vilken det dynamiska elementet (4) kommer att oscillera längs den första huvudaxeln (y), eller en andra rotat- ionsposition, i vilken det dynamiska elementet (4) kommer att oscillera längs den andra huvudaxeln (z), beroende på vibration- ens frekvens, kännetecknad av att anordningen innefattar en positionerings- mekanism som är utformad att positionera det dynamiska elemen- tet i en neutral rotationsposition, som skiljer sig från den första rotationspositionen och den andra rotationspositionen, när struk- turen inte vibrerar. 10 15 20 25 30 35
2. En vibrationsabsorptionsanordning enligt krav 1, varvid det dynamiska elementet (4) innefattar ett elastiskt element (6) som sträcker sig längs rotationsaxeln (x).
3. En vibrationsabsorptionsanordning enligt krav 2, varvid det elastiska elementet (6) tillhandahåller nämnda olika rörelsemot- stånd.
4. En vibrationsabsorptionsanordning enligt något av kraven 2 och 3, varvid det dynamiska elementet (4) har ett masselement (7), som är anordnat på det elastiska elementet (6) och bildar en dynamisk massa.
5. En vibrationsabsorptionsanordning enligt krav 4, varvid masselementet (7) tillhandahåller nämnda olika rörelsemotstånd.
6. En vibrationsabsorptionsanordning enligt något av kraven 2 till 5, varvid det elastiska elementet (6) innefattar ett mellanlig- gande segment (6a), ett första yttre segment (6b) och ett andra yttre segment (6c), vilka sträcker sig längs rotationsaxeln (x) och är roterbara i förhållande till varandra och till fästet (2).
7. En vibrationsabsorptionsanordning enligt krav 6, varvid det första yttre segmentet (6b) och det andra yttre segmentet (6c) är mekaniskt kopplade med varandra.
8. En vibrationsabsorptionsanordning enligt något av de före- gående kraven, varvid vibrationsabsorptionsanordningen innefat- tar två rotationslager (5), vilka är monterade på fästet (2) och så- ledes är mekaniskt förbundna med strukturen (1), och varvid det dynamiska elementet (4) vid respektive ände av detsamma är lag- rat i de två rotationslagren (5) för att vara roterbart runt rotations- axeln (x).
9. En vibrationsabsorptionsanordning enligt krav 8, varvid åt- minstone ett av rotationslagren (5) innefattar ett spetslager. 10 15 20 25 30
10. En vibrationsabsorptionsanordning enligt något av de före- gående kraven, varvid positioneringsmekanismen innefattar en vikt (11) anordnad på det dynamiska elementet (4) för att rotera det dynamiska elementet (4) till den neutrala rotationspositionen när strukturen (1) inte vibrerar.
11. En vibrationsabsorptionsanordning enligt något av de före- gående kraven, varvid positioneringsmekanismen innefattar ett fjäderarrangemang (12) som verkar på det dynamiska elementet (4) för att rotera det dynamiska elementet (4) till den neutrala ro- tationspositionen när strukturen (1) inte vibrerar.
12. En vibrationsabsorptionsanordning enligt krav 11, varvid fjä- derarrangemanget (12) innefattar åtminstone en fjäder (13) för- bunden med det dynamiska elementet (4).
13. En vibrationsabsorptionsanordning enligt krav 12, varvid nämnda åtminstone en fjäder (13) innefattar en fjäder som har en icke-linjär karaktäristik och ett progressivt beteende med ett lågt moment för låg rotation hos det dynamiska elementet (4) och ett väsentligt högre moment vid en viss rotation hos det dynamiska elementet (4).
14. En vibrationsabsorptionsanordning enligt något av de före- gående kraven, varvid positioneringsmekanismen innefattar ett magnetarrangemang (14) som verkar på det dynamiska elementet (4) för att rotera det dynamiska elementet (4) till den neutrala ro- tationspositionen när strukturen (1) inte vibrerar.
15. En vibrationsabsorptionsanordning enligt krav 14, varvid magnetarrangemanget (14) innefattar en första magnet (15) för- bunden med det dynamiska elementet (4) och en andra magnet (16, 17) förbunden med fästet (2).
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE1451045A SE538004C2 (sv) | 2014-09-09 | 2014-09-09 | A vibration absorbing device for reducing vibrations and sounds in a structure |
EP15756933.6A EP3191734B1 (en) | 2014-09-09 | 2015-09-04 | A vibration absorbing device for reducing vibrations and sounds in a structure |
PCT/EP2015/070209 WO2016037933A1 (en) | 2014-09-09 | 2015-09-04 | A vibration absorbing device for reducing vibrations and sounds in a structure |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
SE1451045A SE538004C2 (sv) | 2014-09-09 | 2014-09-09 | A vibration absorbing device for reducing vibrations and sounds in a structure |
Publications (2)
Publication Number | Publication Date |
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SE1451045A1 true SE1451045A1 (sv) | 2016-02-09 |
SE538004C2 SE538004C2 (sv) | 2016-02-09 |
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Application Number | Title | Priority Date | Filing Date |
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SE1451045A SE538004C2 (sv) | 2014-09-09 | 2014-09-09 | A vibration absorbing device for reducing vibrations and sounds in a structure |
Country Status (3)
Country | Link |
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EP (1) | EP3191734B1 (sv) |
SE (1) | SE538004C2 (sv) |
WO (1) | WO2016037933A1 (sv) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
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EP3985278B1 (fr) * | 2019-04-25 | 2023-10-25 | Saint-Gobain Placo | Elément de construction à absorbeurs de résonance |
FR3095461B1 (fr) * | 2019-04-25 | 2021-03-26 | Saint Gobain Placo | Absorbeur de résonance pour une paroi de construction |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3614126A (en) * | 1969-08-11 | 1971-10-19 | Norman C Carlson | Stabilizing device for automotive vehicles |
US5873559A (en) | 1997-04-17 | 1999-02-23 | Applied Power Inc. | Adaptively tuned vibration absorber for reduction of aircraft cabin noise |
AU2003233607A1 (en) * | 2002-05-21 | 2003-12-12 | Bell Helicopter Textron Inc. | Variable stiffness support |
US20040134733A1 (en) | 2003-01-13 | 2004-07-15 | Wood James Gary | Vibration absorber |
WO2006083222A1 (en) | 2005-02-02 | 2006-08-10 | A2 Acoustics Ab | A device for reducing vibrations and sounds |
SE528267C2 (sv) | 2005-02-02 | 2006-10-10 | A2 Acoustics Ab | Anordning för reducering av vibration och ljud |
-
2014
- 2014-09-09 SE SE1451045A patent/SE538004C2/sv not_active IP Right Cessation
-
2015
- 2015-09-04 WO PCT/EP2015/070209 patent/WO2016037933A1/en active Application Filing
- 2015-09-04 EP EP15756933.6A patent/EP3191734B1/en active Active
Also Published As
Publication number | Publication date |
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WO2016037933A1 (en) | 2016-03-17 |
EP3191734B1 (en) | 2020-02-26 |
SE538004C2 (sv) | 2016-02-09 |
EP3191734A1 (en) | 2017-07-19 |
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