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The present invention relates to a vehicle acoustic device that utilizes various panel members for
interior and exterior of a vehicle as an acoustic diaphragm. Examples of conventional vehicle
acoustic devices include those shown in FIGS. 1 to 3 (Japanese Patent Application No. 54135114. First, FIG. 1 shows a driver D which is an acoustic vibrator. The excitation plate (2) and
the cover plate (3) are fixed to both end faces of the forearm (upper and lower sides in FIG. 1) of
the cylindrical frame +1) to constitute a case body. A yoke (5) with an i gunsoto (4) is arranged.
The yoke (5) comprises a pole piece (5a) and a yoke play (5b), which are integrated with the
magnet (4) to form a magnetic circuit having an air gap, and the yoke play (5b) It is elastically
supported by the frame (1) via a damper (6) at a portion. Further, a coil (7) wound around a
bobbin is disposed in the gap portion, and the bobbin is fixed to the vibrating plate (2). Then, as
shown in FIGS. 2 and 3, the driver D configured in this manner is screwed at a portion of 7
frames (1) on the back side of a panel member (8) forming a vehicle cover or the like of a car. Is
attached. As described above, in the vehicle acoustic device, the driver D is directly attached to
the panel member (8) for the interior and exterior of the automobile, and the entire panel
member (8) is used as it is as an acoustic diaphragm. As the acoustic diaphragm, a wall plate or
the like of a room is also used for the slack of the interior and exterior members of an automobile
as shown in the illustrated example, and such a panel member (8) etc. is made of a material such
as compressed cardboard or veneer. Generally, it is rigidly fixed to a vehicle body or the like at its
outer edge or the like. When the voice signal is supplied to the coil (7), the magnet (4) side and
the frame (1) side, that is, the excitation plate (2) side vibrates relative to each other through the
damper (6). The panel member (8) is vibrated by the vibration of the vibration plate (2) or the
like, and the bass region is reproduced. However, in such a conventional panel speaker, since the
entire panel member (8) is used as an acoustic diaphragm as it is, plate vibration with a fixed
portion as a node is performed to have a plurality of natural resonance points. This inherent
resonance causes a peak and dip in the reproduction output as shown in the reproduction
frequency characteristic of FIG. 4, resulting in a problem that the appropriate reproduction
bandwidth becomes narrow. Further, there is a problem that divided vibration occurs in which
each part of the panel member (8) vibrates in different phases, the output sound pressure level is
low, the efficiency is lowered, and the transient response characteristic is also bad.
The present invention has been made in view of such conventional problems, and a plurality of
appropriately shaped slits are continuously provided so as to surround a required area portion to
be functioned as a diaphragm, and rigidity is increased in the required area portion. It is an
object of the present invention to provide a vehicle acoustic device that solves the abovementioned problems by attaching a separate diaphragm member. The present invention will be
described below based on the drawings. 5 and 6 show an embodiment of the present invention.
The same or equivalent parts as those shown in FIGS. 1 to 3 in the drawings of FIG. First of all, in
the present invention, a separate diaphragm member (12m) for increasing rigidity etc. is attached
to the vibrating portion (8b) to which the driver D, which is an acoustic vibrator, is attached. The
vibrating portion (8b) consisting of 8) and the diaphragm member (12a) are integrated to
constitute a diaphragm 02 in a panel speaker. The diaphragm member (12a) may be made of any
appropriate material as long as it can increase the rigidity and mass of the vibrating portion (8b).
A laminated material such as DYLARK (trade name) or a metal plate such as At is used as an
example Be done. Next, the operation will be described. When an audio signal is supplied to the
coil (7), the magnet (4) side and the excitation plate (2) side in the driver D relatively vibrate
through displacement via the damper (6), and this vibration causes vibration. The plate 0 is
excited to generate sound pressure, and the bass range is reproduced. At this time, since the
diaphragm (the mass and the stiffness of the thirst are both increased by the required amount,
the lowest resonance frequency f0 is lowered by the required value as apparent from the display
equation of the lowest resonance frequency fa described later) a3 is this lowest resonance
frequency f. Sound pressure is generated by piston motion vibration at the above frequency.
Therefore, as shown by the solid line in Fig. 7, the reproduction frequency characteristic is
extended further to the low band side as the low band reproduction limit is extended to wide
band and flat characteristics, and the transient response characteristic is improved to improve
the reproduction frequency characteristic as a whole. Ru. Next, the lowest resonance frequency f.
Explain the display expression of. Now town; equal mass of diaphragm system, spring constant of
k1 diaphragm system, magnet system mass of m2 nidriver, k! Assuming that the spring constant
of the driver (damper), ω = 2πf, and the magnet system mass 2 K l 'cos ω [, for the
diaphragm system mass, if an excitation force of −p cos ωt acts, the motion for the diaphragm
system mass When the equation of motion is examined, the equation of motion is 2 (X + X2) 0m2d2x2 / dt2-1-k2 (x2-xt) = F
Further, assuming that the forced vibration is x1 = at cos ω j s xt = axas ω ′ (
ha 2;
amplitude)... (-Town ω "ten k + + k 2) (= m 2 ω" + to +) kz 2) ". Here, since the frequency at
which the lowest resonance frequency f0 and the amplitude a1 become infinite (assuming that
there is no mechanical resistance), the denominator of the above equation (1) is set to zero as
follows (-cho ω "-1-J + kz) (M2ω2 + kz) k22 = O ′ ′ ′ · ω (= 2πf) satisfying the equation (0)
is determined, and it agrees with the higher value of the two solutions. Thus, the lowest
resonance frequency f from the equation 0 with .... Depends on the equivalent mass of the
diaphragm system and its spring constant, etc. For this reason, in the case of FIGS. 5 and 6, since
the imaging plate 07J is attached to the diaphragm member (12a) and the mass thereof is
increased by the required value, this increase is apparent from the above equation (0).
Conversely, the lowest resonance frequency f. Decreases by the required value. As described
above in detail, according to the present invention, since a separate diaphragm member for
increasing rigidity etc. is attached to the required area portion to function as a diaphragm, the
low range reproduction limit further extends to the low range side, and the characteristics The
effect is obtained that the frequency characteristic is improved as a whole and the transient
response characteristic is improved by 1 h and the frequency response is entirely improved.
Brief description of the drawings
FIG. 1 is a partial sectional side view showing a part of a driver in a conventional vehicle acoustic
device, FIG. 2 is a plan view showing a conventional vehicle acoustic device, and FIG. 3 is a side
view of the same vehicle acoustic device 4 is a characteristic curve diagram showing
reproduction frequency characteristics of the vehicle acoustic system, FIG. 5 is a plan view
showing an embodiment of the vehicle acoustic system according to the present invention, and
FIG. FIG. 7 is a characteristic curve diagram showing the reproduction frequency characteristics
of the above embodiment.
8: panel member 8b: vibrating portion 11; slito 11a: plume 12: diaphragm 12a: diaphragm
member V Nidriver (acoustic vibrator) Clarion Corporation also represents Nissan Motor Co., Ltd.
1) Directly Figure 1 Figure 2 Figure 3 Figure 4 Figure 5 Figure 1 Figure 6 Seventh factor
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