TECHNICAL FIELD
[OOO 11
The present invention relates to a soundproof wheel for a railway vehicle, and
particularly to a soundproof wheel for a railway vehicle, which allows for significant
reduction in noise caused by the vibration of the wheel, and is also excellent in
durability.
BACKGROUND ART
[0002]
The noise generated when a railway vehicle travels is a top-priority issue to be
solved for railroad wayside environments. Such noise includes those generated
from wheels. Noise generated from a wheel includes wheel rolling noise and socalled
squeak noise. The squeak noise is mostly generated when a vehicle passes a
curved road having a large curvature. The wheel rolling noise is generated not only
when a vehicle passes a curved road but also when it passes a straight road.
[0003]
The surface of a rail, as well as the surface of a wheel which comes into
contact therewith have minute unevenness. As a result, when the wheel rolls on the
rail, the wheel and the rail are excited, conceivably causing wheel rolling noise. It
is also conceived that the squeak noise is attributable to the vibration of the wheel.
Moreover, a peculiar wheel noise occurs in such a way that: when there is a portion
that has wave-like wear (hereafter, referred to as "wavy wear") on a tread part, which
is a portion to come into contact with the wheel, in the rail, and if the vehicle passes
on such a worn portion, the wheel is severely excited, thus causing noise.
[0004]
To reduce the noise generated by the vibration of a wheel (hereafter, referred
to as "wheel vibration noise"), Patent Literatures 1 and 2 have proposed a soundproof
wheel in which a soundproofing device is attached to an inner peripheral side of a
rim section of the wheel. Such a soundproof wheel is equipped with a
soundproofing device which is composed of a combination of an elastic body section
such as rubber and an additional mass section and is attached to an attachment
groove formed in an inner peripheral surface of the rim section with a metal
attachment.
[0005]
Such a soundproofing device is considered to act as a dynamic vibration
absorber. A dynamic vibration absorber has a resonance frequency, which
coincides with a natural frequency of a structure, and can absorb (reduce) the
vibration of the structure through resonance. Therefore, by attaching such a
soundproofing device to a wheel, it is possible to reduce the noise due t i natural
vibration of the coinciding frequency. The resonance frequency f of a
soundproofing device is given by:
f = (112x) x (klm)'" ...( 1)
where n is the circular constant, k is a spring constant of the elastic body section, and
m is the mass of the additional mass section. Therefore, given a natural frequency
of a wheel, it is possible to determine the spring constant k and the mass m of the
additional mass section from Formula (1) such that the resonance frequency f of the
soundproofing device coincides with the natural frequency.
[0006]
A wheel normally has multiple natural vibration modes, and natural
frequencies corresponding to those natural vibration modes. Therefore, a wheel
also has multiple natural frequencies. Patent Literatures 2 and 3 have proposed a
soundproof wheel including a plurality of soundproofing devices each having a
different resonance frequency, in which the resonance frequency of each sound
proofing device coincides with any of the multiple natural frequencies of the wheel.
According to these soundproof wheels, it is possible to concurrently reduce noise
corresponding to multiple natural frequencies.
[0007]
Specifically, in the wheel of Patent Literature 2, two soundproofing devices
are used in which two types of elastic bodies each having a different elastic constant
are used respectively, such that the resonance frequencies of the two soundproofing
devices are different from each other. In the wheel of Patent Literature 3, a
soundproofing device (a dynamic vibration absorber consisting of an elastic body
and an abutment plate) is divided in a circumferential direction of the soundproof
wheel, and an adjustment is made such that each resonance frequency of the divided
soundproofing devices coincides with any of natural frequencies of the wheel. Such
a configuration makes it possible to concurrently absorb noise components
corresponding to two or more levels of frequencies. Further, as a result of being
divided in the circumferential direction of the soundproof wheel, the soundproofing
device disclosed in Patent Literature 3 makes it possible to increase the natural
frequencies of the abutment plate to higher frequencies which will not cause any
problem as noise.
[OOOS]
Among natural vibration modes of a wheel, a primary mode which may cause
wheel rolling noise is one in which the rim section vibrates in an in-plane direction
and the plate section vibrates in an out-of-plane direction. Such noise due to natural
vibrations include at least, 3 levels of frequency components, for example, around 2
kHz, around 3 kHz, and around 4 kHz in a range of 1 kHz to 10 kHz of frequency
ranges to which human auditory sense is sensitive.
[0009]
Meanwhile, when a vehicle is traveling at a high speed, the soundproofing
device is subject to various forces, causing a risk that the soundproofing device falls
off from the wheel. In the inventions according to Patent Literatures 1 to 3,
sufficient measures have not been taken to prevent the soundproofing device from
falling off from the wheel.
[OO 1 01
Patent Literature 4 discloses a soundproofing device including a ring-shape
additional mass section, and an elastic body section attached to an outer peripheral
portion of the additional mass section, in which the elastic body section is disposed
in a groove formed in a rim section.
[OOI 13
The soundproof wheel of Patent Literature 4 is configured such that the elastic
body section is fixed to a bottom portion of a groove formed in the rim section and to
the additional mass section, while the additional mass section is movable with
respect to the rim section. Such configuration allows absorption of vibration of the
wheel.
[OO 1 21
In this soundproofing device, since the opening side of the groove is blocked
by the additional mass section with respect to the elastic body section, the elastic
body section is not likely to fall off from the wheel even if it is separated from the
additional mass section. However, in this invention, when the elastic body section
deteriorates, the displacement of the additional mass section with respect to the rim
sectibn during travelling of the vehicle increases, and the additional mass section
may collide with other members, such as a brake disk. Moreover, as a result of that
the inner surface of the groove of the rim section and the additional mass section are
rubbed against each other, a flaw may occur in the rim section and the additional
mass section, or these members may be won. Further, when the elastic body
section is separated completely, there is possibility that additional mass section falls
off from the wheel. For this reason, a wheel equipped with the soundproofing
device is less durable.
CITATION LIST
PATENT LITERATURE
[OO 131
Patent Literature 1 : Japanese Utility Model No. 2577323
Patent Literature 2: Japanese Patent No. 309783 1
Patent Literature 3: Japanese Patent Application Publication No. 58-1 16202
Patent Literature 4: Japanese Patent Application Publication No. 2006- 182 136
SUMMARY OF INVENTION
TECHNICAL PROBLEM
[00 141
Accordingly, it is an objective of the present invention to provide a
soundproof wheel for a railway vehicle, which allows for significant reduction in
noise caused by the vibration of the wheel, and is also excellent in durability.
SOLUTION TO PROBLEM
[00 1 51
The gist of the present invention is a soundproof wheel described in the
following (A):
(A) A soundproof wheel for a railway vehicle, including
a soundproofing device mounted onto an inner peripheral surface of a rim
section of the wheel,
the soundproofing device including:
a fixing ring fitted in a groove at least in an outer peripheral portion of the
fixing ring, the groove being formed in the inner peripheral surface of the rim section
and opened toward a central axis of the wheel, the fixing ring being fixed to the rim
section;
an elastic body section which is adhered to an outer peripheral surface of the
fixing ring along a circumferential direction of the fixing ring, and is disposed in the
groove; and
an additional mass section which is adhered to an opposite side of the elastic
body section with respect to the fixing ring, and is disposed in the groove, wherein
the elastic body section includes a plurality of elastic body pieces disposed
along the circumferential direction of the fixing ring,
the additional mass section includes a plurality of additional mass pieces
which are spaced apart from each other in the circumferential direction of the fixing
ring, each additional mass piece being adhered to any of the plurality of elastic body
pieces,
the wheel has multiple natural frequencies corresponding to multiple natural
vibration modes,
the soundproofing device includes a plurality of dynamic vibration absorbers,
each dynamic vibration absorber having the elastic body piece, and the additional
mass piece adhered to the elastic body piece, and
at least one dynamic vibration absorber of the plurality of dynamic vibration
absorbers has a resonance frequency different from the resonance frequencies of the
other dynamic vibration absorbers, and any of the resonance frequencies of the
plurality of dynamic vibration absorbers corresponds to any of the multiple natural
frequencies.
[00 161
Note that the width of the elastic body section in the axial direction of the
soundproofing device is preferably not less than 5 mm and not more than 10 mm. In
that case, the width of the additional mass section in the axial direction of the
soundproofing device is preferably not less than 5 mm and not more than 10 mm.
[OO 171
In a cross section containing the axis of the soundproof wheel,
the groove includes:
a first portion having a width equal to a minimum width of the fixing ring, or
larger than the minimum width, and
a second portion formed nearer a bottom of the groove with respect to the first
portion, and having a width smaller than the minimum width of the fixing ring.
[OO 181
The soundproof wheel preferably includes a protrusion interposed between
the dynamic vibration absorbers adjacent to each other in the circumferential
direction, and protruding from the outer peripheral surface of the fixing ring.
[OO 1 91
When the soundproof wheel includes the protrusion, a distal end of the
protrusion is preferably in contact with the bottom of the groove.
ADVANTAGEOUS EFFECTS OF INVENTION
[0020]
According to the present invention, due to the configuration that the fixing
ring is fixed to the rim section of the wheel, the vibration of the wheel is transmitted
to the plurality of dynamic vibration absorbers (elastic body pieces and additional
mass pieces) through the fixing ring. Since at least one dynamic vibration absorber
of the plurality of dynamic vibration absorbers has a resonance frequencx different
from the resonance frequencies of the other dynamic vibration absorbers, the
resonance frequency of each dynamic vibration absorber corresponds to any of the
multiple natural frequencies of the wheel, it is possible to concurrently reduce noise
corresponding to natural frequencies of not less than 2 levels, thereby significantly
reducing wheel vibration noise.
[002 11
Moreover, according to the present invention, the elastic body section and the
additional mass section are disposed in the groove of the rim section, and a fixing
ring fixed to the rim section lies at an opening side of the groove with respect to the
elastic body section and the additional mass section. As a result, even if an
additional mass section is separated from the elastic body section, or an elastic body
section is separated from the fixing ring, it is not likely that those separated elastic
body section and additional mass section fall off the soundproof wheel.
[0022]
Further, due to the configuration that the fixing ring which is one of the
components constituting the soundproofing device is fixed to the rim section of the
wheel, there will be no rubbing between the soundproofing device and the rim
section of the wheel. Furthermore, even if the elastic body section deteriorates,
resulting in decline in elasticity thereof, the additional mass section will not collide
with any member other than the rim section. Therefore, the soundproof wheel is
highly durable.
BRIEF DESCRIPTION OF DRAWINGS
[0023]
[FIG. 1 A] FIG. 1A is a sectional view of a soundproof wheel according to an
embodiment of the present invention, showing one side portion of the soundproof
wheel with respect to its central axis.
[FIG. I B] FIG. 1 B is an enlarged view of a region shown by a circle C in FIG.
I A.
[FIG. 21 FIG. 2 is a plan view to show an example of a soundproofing device
which can be used for a soundproof wheel of the present invention.
[FIG. 31 FIG. 3 is a plan view to show another example of a soundproofing
device which can be used for a soundproof wheel of the present invention.
[FIG. 4A] FIG. 4A is a sectional view of a soundproof wheel according to a
first variation of the embodiment shown in FIG. 1A to FIG. 3.
[FIG. 4B] FIG. 48 is a sectional view of a soundproof wheel according to a
second variation of the embodiment shown in FIG. 1A to FIG. 3.
[FIG. 5A] FIG. 5A is a sectional view of a soundproof wheel according to a
third variation of the embodiment shown in FIG. 1A to FIG. 3.
[FIG. 5B] FIG. 5B is a sectional view of a soundproof wheel according to a
fourth variation of the embodiment shown in FIG. 1A to FIG. 3.
[FIG. 61 FIG. 6 is a schematic diagram to show a configuration of a wheel
rolling noise tester.
[FIG. 71 FIG. 7 is a diagram to show noise correction levels to be used when
performing noise analysis.
[FIG. 83 FIG. 8 is a diagram showing a relationship between a 113 octave
band center frequency and a noise level for Examples 1 to 4 and Comparative
Example 1.
[FIG. 91 FIG. 9 is a diagram showing a relationship between a 113 octave
band center frequency and a noise level for Comparative Examples 1 to 5.
[FIG. 101 FIG. 10 is a diagram showing a relationship between a
circumferential speed of the rail wheel and a noise level for Examples 1 to 4, and
Comparative Example 1.
[FIG. 1 11 FIG. 11 is a diagram showing a relationship between a
circumferential speed of rail wheel and a noise level for Comparative Examples 1 to
5.
DESCRIPTION OF EMBODIMENTS
[0024]
Hereafter, embodiments of the present invention will be described in detail
with reference to the appended drawings.
COO251
FIGS. 1 A and 1B are sectional views of a soundproof wheel according to an
embodiment of the present invention, in which FIG. 1A shows one side portion of
the soundproof wheel with respect to its central axis, and FIG. 1 B shows an enlarged
view of a region shown by a circle C in FIG. 1A.
[0026]
The soundproof wheel 1, which is used for railway vehicles, includes a wheel
2 and a soundproofing device 3. The wheel 2 includes an annular plate section 4,
and an annular rim section 5 located in an outer peripheral portion of the plate
section 4. The rim section 5 protrudes to both sides in the thickness direction of the
plate section 4 with respect to the plate section 4, and has an inner peripheral surface
6 which faces a central axis A of the soundproof wheel 1. In an outer peripheral
surface of the rim section 5, a flange 7 protrudes, at one side with respect to the
direction along the central axis A, in the opposite direction to the central axis A.
[0027]
In the rim section 5, a groove 8, which opens up in the central axis A direction,
is formed in an annular shape around the central axis A in the inner peripheral
surface 6 on one side (the same side of the flange 7) with respect to the direction
along the central axis A. The soundproofing device 3 is fitted in the groove 8 over
the entire circumference of the groove 8.
[0028]
The soundproofing device 3 includes a fixing ring 10, an elastic body section
1 1 adhered to an outer peripheral surface 10a of the fixing ring 10, and an additional
mass section 12 adhered to an opposite side of the elastic body section I I with
respect to the fixing ring 10. The fixing ring 10 is made of a high rigidity material
such as a metal. The fixing ring 10 has an outer peripheral side portion in the radial
direction to be fitted in the groove 8 and fixed to the rim section 5. The fixing of
the fixing ring 10 to the rim section 5 can be performed by, for example, welding,
caulking, bonding, etc.
[0029]
A width (length in an axial direction of the soundproofing device 3) of the
fixing ring 10 is about the same as a width of the groove 8, and the opening part of
the groove 8 is sealed by the fixing ring 10. The elastic body section 1 I and the
additional mass section 12 are disposed in this sealed space in the groove 8.
[0030]
The elastic body section 11 is made of, for example, rubber. The vibration
generated in the wheel 2 during travelling of a vehicle is transmitted to the elastic
body section 1 1 and the additional mass section 12 through the fixing ring 10,
thereby causing the elastic body section 11 and the additional mass section 12 to
vibrate. A gap is formed between the elastic body section 11 and an inner surface
of the groove 8 and between the additional mass section 12 and the inner surface of
the groove 8 such that the elastic body section 1 I and the additional mass section 12
will not come into contact with the inner surface of the groove 8 even if they are
caused to vibrate.
. -
[003 11
The elastic body section 1 1 and the additional mass section 12 are disposed in
the groove 8 of the rim section 5, and a fixing ring 10 fixed to the rim section 5 lies
at an opening side of the groove 8 with respect to the elastic body section 1 1 and the
additional mass section 12. As a result, even if the additional mass section 12 is
separated from the elastic body section 1 1, or the elastic body section 11 is separated
from the fixing ring 10, it is not likely that those separated elastic body section 11
and additional mass section 12 fall off the soundproof wheel 1.
[0032]
Due to the configuration that the fixing ring 10 which is one of the
components constituting the soundproofing device 3 is fixed to the rim section 5 of
the wheel 2, there will be no rubbing between the soundproofing device 3 and the
rim section 5 of the wheel 2. Further, even if the elastic body section I I
deteriorates, resulting in a decline in elasticity thereof, the additional mass section 12
will not collide with any member other than the rim section 5. Therefore, the
soundproof wheel 1 is highly durable.
[0033]
FIG. 2 is a plan view to show an example of the soundproofing device 3.
The elastic body section 1 1 includes a plurality of elastic body pieces 13
spaced apart from each other in a circumferential direction of the soundproofing
-Kdevice
3. The additional mass section 12 includes a plurality of additional mass
pieces 14 spaced apart from each other in the circumferential direction of the
soundproofing device 3. In the example of FIG. 2, the elastic body section 11
includes 12 elastic body pieces 13, and the additional mass section 12 includes 12
additional mass pieces 14. Each additional mass piece 14 is adhered to any of the
elastic body pieces 13.
[0034]
Each elastic body piece 13 and the additional mass piece 14 adhered to the
elastic body piece 13 constitute a dynamic vibration absorber 15. In the example of
FIG. 2, the soundproofing device 3 includes 12 dynamic vibration absorbers 15A to
15L. Regarding the circumferential direction of the soundproofing device 3, each
dynamic vibration absorber 15 has a substantially flush end face.
[0035]
The wheel 2 normally has multiple natural frequencies respectively
corresponding to multiple natural vibration modes. At least one dynamic vibration
absorber 15 of the dynamic vibration.absorbers 15A to 15L has a resonance
frequency different From that of another dynamic vibration absorber 15. That is, the
dynamic vibration absorbers 15A to 15L have at least two resonance frequencies.
Any of the resonance frequencies of the dynamic vibration absorbers 15A to 15L
coincides with any of the natural fiequencies of the wheel 2. As a result, it is
possible to concurrently reduce noise corresponding to at least two natural
frequencies, among the multiple natural frequencies of the wheel 2.
[0036]
The dynamic vibration absorbers 15A to 15L preferably have at least three
resonance frequencies, each of which coincides with any natural frequency of the
wheel 2. This makes it possible to efficiently reduce noise of the wheel 2.
[0037]
As described above, wheel rolling noise due to natural vibrations of the plate
section 4 and the rim section 5 is generated from the wheel 2. Such noise includes,
for example, frequency components of 2.0 kHz, 2.5 kHz, and 3.0 kHz in frequency
ranges to which human auditory sense is sensitive, for example, a range of 1 kHz to
10 kHz.
In this case, for example, the dynamic vibration absorbers 15A to 15L can be
divided into a first to third groups such that the dynamic vibration absorbers 15
belonging to the first group each have a resonance frequency of 2.0 kHz, the
. dynamic vibration absorbers 15 belonging to the second group each have a resonance
frequency of 2.5 kHz, and the dynamic vibration absorbers 15 belonging to the third
group each have a resonance frequency of 3.0 kHz. As a result, it is possible to
significantly reduce noise in auditory sense. The first to third groups can be each
made up of 4 dynamic vibration absorbers 15.
[0039]
Moreover, configuring any of the dynamic vibration absorbers 15A to 15L to
have a resonance frequency corresponding to a frequency of squeak noise makes it
possible to reduce the squeak noise. Similarly, configuring any of the dynamic
vibration absorbers 15A to 15L to have a resonance frequency corresponding to a
frequency of noise attributable to wavy wear makes it possible to reduce such noise.
[0040]
It is possible to obtain a desired value for each resonance frequency of the
dynamic vibration absorbers 15A to 15L by setting appropriate values for the spring
constant k of the elastic body piece 13 and the mass m of the additional mass piece
14 based on Formula (I).
[004 11
The soundproof wheel 1 can be produced by first providing the soundproofing
device 3 with a disconnected part in the circumference thereof, and after fitting the
additional mass section 12, the elastic body section 11, and an outer peripheral
portion of the fixing ring I0 in the groove 8 of the rim section 5, joining the
disconnected section of the soundproofing device 3 by, for example, welding.
[0042]
Regarding the axial direction of the soundproofing device 3, the length of the
elastic body section 1 I (each elastic body piece 13) is not less than 5 mm and not
more than 10 mm, and the length of the additional mass section 12 (each additional
mass piece 14) is not less than 5 mm and not more than 10 mm. By arranging the
elastic body section 11 and the additional mass section 12 to have such sizes, it
becomes easy to attach them to the fixing ring 10, and to adjust their resonance
frequencies.
[0043]
The number of the dynamic vibration absorbers 15 may be other than 12, for
example, 24 as shown in FIG. 3. In this case, since the number of the dynamic
vibration absorbers 15 increases compared with the soundproofing device 3 of FIG. 2,
it is possible to increase the number of corresponding resonance frequencies of the
wheel 2. Moreover, since even when the elastic body piece 13 of some of the
dynamic vibration absorbers 15 deteriorates, resulting in deterioration of the
performance as the dynamic vibration absorber 15, vibration can be reduced by other
dynamic vibration absorbers 15, it is possible to suppress deterioration of the
vibration control (rolling noise reduction) performance of the wheel 2. It becomes
easier to obtain such effect as the number of the dynamic vibration absorbers 15
Increases.
[00441
On the other hand, since increase in the number of the dynamic vibration
absorbers 15 results in decrease in the lengths of the additional mass pieces 14 and
the elastic body pieces 13 in the circumferential direction of the wheel 2, it may
become more likely that the additional mass piece 14 is separated from the fixing
ring 10 due to deterioration of the elastic body piece 13. By decreasing the number
of the dynamic vibration absorbers 15, and increasing the lengths of the additional
mass pieces 14 and the elastic body pieces 13 in the circumferential direction of the
wheel 2, it is possible to make such separation less likely to occur. However, since
the additional mass piece 14 will remain in the groove 8 sealed by the fixing ring 10
even if it is separated from the fixing ring 10, the possibility that it falls off will be
very low.
[0045]
FIG. 4A is a sectional view of a soundproof wheel according to a first
variation of the embodiment shown in FIG. IA to FIG. 3, showing a section
including the central axis of the wheel. In FIG. 4A, components corresponding to
those shown in FIG. 1 B are given the same reference symbols as those of FIG. 1 B,
thus omitting description thereof.
[0046]
In this soundproof wheel, a groove 8A which is opened toward the central
axis of the wheel is formed in a rim section 5 of the wheel. A fixing ring 10
included in the soundproofing device 3 is fitted in the groove 8A. As a result, a
sealed space is formed in the groove 8A, and the elastic body section 11 and the
additional mass section 12 are disposed in the sealed space in the groove 8A.
[0047]
The fixing ring 10 has a substantially constant width. The groove 8A
includes a first portion 8A1, and a second portion 8A2 which is formed nearer the
bottom of the groove 8A with respect to the first portion 8Al. The first portion 8A1
has a width substantially equal to the width of the fixing ring 10 (minimum width).
The second portion 8A2 has a width smaller than the width of the fixing ring 10. In
this embodiment, both of the widths of the first and second portions 8A 1 and 8A2 are
substantially constant, and a step 8s is formed in an inner wall of the groove 8A
between the first portion 8A 1 and the second portion.8A2.
[0048]
The fixing ring 10 is fixed to the rim section 5 in a state of being in contact
with the step 8s. As a result of the second portion 8A2 having a width smaller than
the width of the fixing ring 10, the fixing ring 10 cannot move closer to a bottom
face of the groove 8A from a state of being in contact with the step 8s. Therefore,
in this state, the interval between the fixing ring 10 and the bottom face of the groove
8A is kept constant. This interval is set such that the additional mass section 12 and
the bottom face of the groove 8A are spaced apart by not less than a constant
distance (for example, 1 mm, and preferably 2 mm) even when the additional mass
section 12 moves closer to the bottom face of the groove 8A by vibration. As a
result, it is possible to avoid a situation in which the additional mass section 12 and
the bottom face of the groove 8A come into contact with each other, disabling the
elastic body section 1 1 and the additional mass section 12 to function as the dynamic
vibration absorber.
[0049]
FIG. 4B is a sectional view of a soundproof wheel according to a second
variation of the embodiment shown in FIG. 1A to FIG. 3, showing a section
including the central axis of the wheel. In FIG. 4B, components corresponding to
those shown in FIG. 1B are given the same reference symbols as those of FIG. 1 B,
thus omitting description thereof.
[OOSO]
In this soundproof wheel, a groove 8B which is opened toward the central
axis of the wheel is formed in a rim section 5 of the wheel. A fixing ring 10A
included in a soundproofing device 3A is fitted in the groove 8B. As a result, a
sealed space is formed in the groove 8B, and an elastic body section 1 1 and an
additional mass section 12 are disposed in the sealed space in the groove 8B.
[005 11
The groove 8B has a trapezoidal shape in this section, and its width becomes
smaller as moving closer to the bottom of the groove 89. The fixing ring 10A has a
trapezoidal shape in this section, and the length of the upper base is the minimum
width Wmin. The groove 8B includes a first portion 891, and a second portion 8B2
which is formed nearer the bottom of the groove 89 with respect to the first portion
8B 1. .The first portion 8B 1 has a width equal to the minimum width Wmin of the
fixing ring 10, or a width larger than the minimum width Wmin. The second
portion 882 has a width smaller than the minimum width Wmin of the fixing ring 10.
[0052]
The angle formed by a pair of inner walls of the groove 8B is substantially
equal to the angle formed by a pair of side faces of the fixing ring 10A. The fixing
ring 10A is fitted in the groove 8B with its face having a minimum width being
oriented toward the bottom face of the groove 8B. The side face of the fixing ring
10A is in contact with the inner wall of the groove 8B over substantially the entire
surface.
[0053]
As a result of that the second portion 8B2 has a width smaller than the
minimum width Wmin of the fixing ring IOA, the fixing ring 10A cannot move
closer to the bottom face of the groove 8B from a state in which its side faces are in
contact with the inner walls of the groove 8B. Therefore, in this state, the interval
between the fixing ring 10A and the bottom face of the groove 8B is kept constant.
Therefore, appropriately setting this interval will make it possible, as in the first
variation, to avoid a situation in which the additional mass section 12 and the bottom
face of the groove 8B come into contact with each other, disabling the elastic body
section 11 and the additional mass section 12 to function as the dynamic vibration
absorber.
100541
FIG. 5A is a sectional view of a soundproof wheel according to a third
variation of the embodiment shown in FIG. 1A to FIG. 3, showing a section
perpendicular to the central axis of the wheel. In FIG. 5A, components
corresponding to those shown in FIG. 2 are given the same reference symbols as
those of FIG. 2, thus omitting description thereof.
[0055]
A protrusion 18A protruding from the outer peripheral surface of the fixing
ring 10 is provided between the dynamic vibration absorbers 15 adjacent to each
other in the circumferential direction. The protrusion 18A is fixed to the fixing ring
10, and extends to between the additional mass pieces 14 adjacent to each other in
the circumferential direction. This embodiment is configured such that the height
of the protrusion 18A fiom the outer peripheral surface of the fixing ring 10 is
slightly smaller than the height of the dynamic vibration absorber 15 fiom the outer
peripheral surface of the fixing ring 10.
[005 61
The dynamic vibration absorber 15 and the protrusion 18A are sufficiently
spaced apart such that the dynamic vibration absorber 15 will not come into contact
with the protrusion 18A even if the dynamic vibration absorber 15 vibrates.
Therefore, there will be no case that the dynamic vibration absorber 15 and the
protrusion 18A come into contact with each other, impairing the function of the
dynamic vibration absorber 15.
[0057]
When the protrusion 18A is not provided, if the elastic body piece 13 breaks
off, problems arise in that as a result of the additional mass piece 14 moves in the
groove 8, abnormal noise occurs, and dynamic balance during rotation of the wheel
is disturbed. Such problems can be made less likely to occur in the embodiment of
FIG. 5A, since the additional mass pieces 14 are restricted from moving in the
circumferential direction of the wheel as a result of provision of the protrusion 18A.
[OOS 81
The protrusion 18A may be integral with the fixing ring 10, or a separate body.
When the protrusion 18A is a separate body from the fixing ring 10, the protrusion
18A may be made of, for example, the same material as that of the elastic body piece
13. In this case, the elastic body piece 13 and the protrusion 18A can be formed
collectively. Specifically, it is possible to form an elastic body piece 13 and a
protrusion 18A collectively by disposing a mold formed with concave parts
corresponding to the elastic body piece 13 and the protrusion 18A over the entire
circumference on the outer peripheral surface of the fixing ring 10, poring liquid
precursor, which provides raw material for the elastic body piece 13 and the
protrusion 18A, into the concave part, and thereafter causing the precursor to be
hardened.
[0059]
In this production method, the liquid precursor may intrude into between the
outer peripheral surface of the fixing ring 10 and the mold, thereafter being hardened
as-is. In this case, the elastic body piece 13 and the protrusion 18A will not be
separated completely, and is formed to be connected with a thin film of elastic body.
However, even in this case, each dynamic vibration absorber 15 has a resonance
frequency as designed and vibrates in a mutually independent manner. That is, the
plurality of elastic body pieces 13 exhibit substantially same behavior as in the case
in which they are spaced apart from each other in the circumferential direction of the
fixing ring 10. Therefore, each dynamic vibration absorber can absorb vibration of
a predetermined frequency.
[0060]
FIG. 5B is a sectional view of a soundproof wheel according to a fourth
variation of the embodiment shown in FIG. 1A to FIG. 3, showing a section
perpendicular to the central axis of the wheel. In FIG. 5B, components
corresponding to those shown in FIG. 2 are given the same reference symbols as
those of FIG. 2, thus omitting description thereof.
1006 11
A protrusion 18B protruding from the outer peripheral surface of the fixing
ring 10 is provided between the dynamic vibration absorbers 15 adjacent to each
other in the circumferential direction. The protrusion 18B is fixed to the fixing ring
10, and extends through between the additional mass pieces 14 adjacent to each other
in the circumferential direction. The distal end (the hrthest portion from the outer
peripheral surface of the fixing ring 10) of the protrusion 18B is in contact with the
bottom face of the groove 8. As a result of the protrusion 18B being provided, it
becomes possible, as in the embodiment shown in FIG. 5A, to restrict the additional
mass piece 14 from moving in the circumference direction of the wheel when the
elastic body piece 13 breaks off, thereby suppressing occurrence of abnormal noise,
as well as making it easier to keep dynamic balance during rotation of the wheel.
[0062]
Although the protrusion 18B may be integral with the fixing ring 10, or a
separate body, it is made of a high rigidity material, in either case. As a result, the
interval between the fixing ring'l0 and the bottom face of the groove 8 is kept
constant. This interval is set such that even if the additional mass piece 14 is moved
close to the bottom face of the groove 8 by vibration, the additional mass piece 14
and the bottom face of the groove 8 are spaced apart by not less than a constant
distance (for example, I mm, and preferably 2 mm). As a result, it is possible to
avoid a situation in which the additional mass piece 14 and the bottom face of the
groove 8 come into contact with each other, disabling the hnction of the dynamic
vibration absorber 15. In this point, the embodiment of FIG. 5B can achieve same
effects as those of the embodiment shown in FIGS. 4A and 4B.
EXAMPLES
[0063]
A test using a wheel rolling noise tester was conducted on soundproof wheels
which were examples of the present invention, and wheels which were comparative
examples not satisfying part of the requirements of the present invention, to
investigate noise to be generated.
[0064]
As Examples 1 to 4, soundproof wheels 1 which each includes a
soundproofing device 3 having the structure shown in FIG. 2, and in which each
dynamic vibration absorber 15A to 15L was any of three types (TYPE-i to TYPE-iii)
having different resonance frequencies were fabricated. The natural frequencies of
the soundproof wheel 1 corresponding to major natural vibration modes of the wheel
2 were 2.0 kHz, 2.5 kHz, and 3.0 kHz.
[0065]
Table 1 shows resonance frequencies of the dynamic vibration absorbers 15 of
each type. Table 2 shows contents of the dynamic vibration absorbers of the
soundproof wheels of Examples, and the wheels of Comparative Examples.
100661
[Table 11
Table 1
I I I
Type of Resonance frequency
soundproofing device (kHz)
[Table 21
Table 2
ith only one kind of
[0068]
While 4 dynamic vibration absorbers 15 of TYPE-i, 4 dynamic vibration
absorbers 15 of TYPE-ii, and 4 dynamic vibration absorbers 15 of TYPE-iii were
used in any of Examples, positional relationships for the 3 types of the dynamic
vibration absorbers 15 were varied from each other among Examples 1 to 4.
[0069]
As Comparative Examples, an ordinary wheel (Comparative Example 1)
having no soundproofing device, a wheel (Comparative Example 2) in which all of
the dynamic vibration absorbers 15A to 15L were of TYPE-i, a wheel (Comparative
Example 3) in which all of the dynamic vibration absorbers 15A to 15L were of
TYPE-ii, a wheel (Comparative Example 4) in which all of the dynamic vibration
absorbers 15A to 15L were of TYPE-iii, and a wheel (Comparative Example 5) in
which in place of the soundproofing device 3, a soundproof ring adopted in Patent
Literature 2 was mounted to the wheel 2 were prepared.
[0070]
FIG. 6 is a schematic diagram to show a configuration of a wheel rolling noise
tester used in the test.
[0071]
The wheel rolling noise tester 21 includes: a bearing 23 for rotatably
supporting an axle 22 attached to a wheel 2 (soundproof wheel 1) to be tested; a
hydraulic jack 24 attached to the bearing 23 and for pressing the bearing 23
downward; a rail wheel 25 configured to abut against an outer peripheral portion of
the wheel 2 supported by the bearing 23 through the axle 22, and to rotate the wheel
2; a bearing 26 for supporting the axle 22 attached to the rail wheel 25; a motor 27
for rotatively driving the axle 22 supported by the bearing 26; a precision noise meter
28 for measuring noise generated from the wheel 2 and generating an electric signal
corresponding to the noise; and a frequency analyzer 29 for receiving input of the
electric signal from the precision noise meter 28, and performing frequency analysis
of the electric signal.
[0072]
When performing test, the axle 22 attached to the wheel 2 and the axle 22
attached to the rail wheel 25 were arranged in parallel with each other; the outer
peripheral surface of the wheel 2 supported by the bearing 23 through the axle 22
was pressed against the outer peripheral surface of the rail wheel 25 supported by the
bearing 26 through the axle 22 by being driven by the hydraulic jack 24; and the rail
wheel 25 was rotated by the motor 27 in this state. As the result, the wheel 2 was
rotated.
[0073]
The precision noise meter 28 was disposed at a position 300 mm away from
the wheel 2, and generated noise was measured by the precision noise meter 28 by
rotating the soundproof wheels 1 of Examples and wheels of Comparative Examples
by the wheel rolling noise tester 21. The circumferential speed of the rail wheel 25
during noise measurement was supposed to be the rotational speed of the wheel 2 at
that time. The circumferential speed of the rail wheel 25 was determined from the
number of revolution of the motor 27 and the diameter of the rail wheel 25 (910 mm
in the wheel rolling noise tester 21). For example, when the number of revolution
of the motor 27 was 1750 rpm, the circumferential speed of the rail wheel 25 was
300 krn/h.
[0074]
Noise measurement was performed by setting the precision noise meter 28 at
FLAT characteristics (without auditory correction) and FAST dynamic
characteristics. After the measurement by the precision noise meter 28, frequency
analysis of noise was performed by the frequency analyzer 29 based on the inputted
signal.
[0075]
FIG. 7 is a diagram to show noise correction levels to be used when analyzing
noise. After applying correction by the characteristic "A" of FIG. 7 on the
measured noise, 1/3 octave band processing was performed to determine frequency
characteristics and Overall values. The results are shown in FIGS. 8 to 1 1.
[0076]
FIG. 8 is a diagram showing the relationship between the 1/3 octave band
center frequency and the noise level for Examples 1 to 4 and Comparative Example I.
FIG. 9 is a diagram showing the relationship between the 1/3 octave band center
frequency and the noise level for Comparative Examples I to 5. The results shown
in FIGS. 8 and 9 are those obtained when the rotational speed of the wheel 2
(circumferential speed of the rail wheel 25) was 200 krnh. Overall values (O.A.)
are shown at near the right end of FIGS. 8 and 9.
[0077]
From FIG. 8, it is seen that all of the soundproof wheels 1 of Examples 1 to 4
were able to significantly reduce noise around 2.0 kHz, 2.5 kHz, and 3.0 kHz
compared with Comparative Examples 1, that is, the case without any soundproofing
device. There was no significant difference observed among Examples I to 4.
That is, there was substantially no difference in noise reduction effect due to the
disposition of the dynamic vibration absorbers 15 of TYPE-i to TYPE-iii adopted in
Examples 1 to 4.
[0078]
In contrast to this, as obvious fi-om FIG. 9, the wheels of Comparative
Examples 2 to 4 were only able to reduce noise around a frequency of one level of
the resonance frequencies of the dynamic vibration absorbers 15, and were not able
to reduce noise at other frequencies. The wheel of Comparative Example 5 showed
less noise reduction effect compared with the soundproof wheels 1 of Examples 1 to
4 at least in the overall value.
[0079]
FIG. 10 is a diagram showing the relationship between the circumferential
speed of the rail wheel 25 and the noise level for Examples 1 to 4, and Comparative
Example 1. FIG. 1 1 is a diagram showing the relationship between the
circumferential speed of the rail wheel 25 and the noise level fir Comparative
Examples 1 to 5. In FIGS. 10 and 1 1, the noise levels are shown by overall values.
[OOSO]
As shown in FIG. 10, compared with the wheel of Comparative Example 1,
that is, a case without any soundproofing device, the soundproof wheels 1 of
Examples 1 to 4 achieved noise level reduction of not less than 5 dB(A) in a low
speed range in which the circumferential speed of the rail wheel 25 was not more
than 130 kmk, and also achieved noise level reduction of not less than 3 dB(A) in a
high speed range of not less than 140 krnh as well.
[008 I]
On the other hand, as shown in FIG. 1 1, there was substantially no noise
reduction effect observed in the wheels of Comparative Examples 2 to 5 compared
with the wheel of Comparative Example 1.
REFERENCE SIGNS LIST
[0082]
Soundproof wheel
Wheel
Soundproofing device
Rim section
Inner peripheral surface
Groove
First portion of groove
Second portion of groove
Fixing ring
Outer peripheral surface
Elastic body section
Additional mass section
Elastic body piece
Additional mass piece
Dynamic vibration absorber
Protrusion

We claim:
1. A soundproof wheel for a railway vehicle, comprising
a soundproofing device mounted onto an inner peripheral surface of a rim
section of the wheel,
the soundproofing device including:
a fixing ring fitted in a groove at least in an outer peripheral portion of the
fixing ring, the groove being formed in the inner peripheral surface of the rim section
and opened toward a central axis of the wheel, the fixing ring being fixed to the rim
section;
an elastic body section which is adhered to an outer peripheral surface of the
fixing ring along a circumferential direction of the fixing ring, and is disposed in the
groove; and
an additional mass section which is adhered to an opposite side of the elastic
body section with respect to the fixing ring, and is disposed in the groove, wherein
the elastic body section incbdes a plurality of elastic body pieces disposed
along the circumferential direction of the fixing ring,
the additional mass section includes a plurality of additional mass pieces
which are spaced apart from each other in the circumferential direction of the fixing
ring, each additional mass piece being adhered to any of the plurality of elastic body
pieces,
the wheel has multiple natural frequencies corresponding to multiple natural
vibration modes,
the soundproofing device includes a plurality of dynamic vibration absorbers,
each dynamic vibration absorber having the elastic body piece, and the additional
mass piece adhered to the elastic body piece, and
at least one dynamic vibration absorber of the plurality of dynamic vibration
absorbers has a resonance frequency different from the resonance frequencies of the
other dynamic vibration absorbers, and any of the resonance frequencies of the
plurality of dynamic vibration absorbers corresponds to any of the multiple natural
frequencies.
2. The soundproof wheel according to claim I , wherein
a width of the elastic body section in an axial direction of the soundproofing
*
device is not less than 5 mm and not more than 10 mm, and
a width of the additional mass section in the axial direction of the
soundproofing device is not' less than 5 mm and not more than 10 mm.
3. The soundproof wheel according to claim 1 or 2, wherein
, in a cmss section containing the axis of the soundproof wheel,
the groove includes:
a first portion having a width equal to a minimum width of the fixing ring, or
larger t h a n e minimum width, and
a second portion formed nearer a ,bottom of the groove with respect to the first
portion, and having a width smaller than the minimum width of the Eixing ring.
4. The soundproof wheel 8ccodng to any of claims 1 to 3, further comprising:
a protrusion interposed between the dynamic vibration absorbers adjacent to
each other in the circumferential~tiona, nd protruding b r nt he outer peripheral
surface of the fixing ring.
5. The soundproof wheel according to claim 4, wherein
a distal end of the protrusion is in contact with a bottom of the groove.