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BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a cross-sectional view showing a cone type
diaphragm, FIG. 2 is a curve showing frequency characteristics of a cone type speaker, and FIGS.
3 a and 3 b are schematic diagrams for explaining a multilayer structure. Fig. 4 and Fig. 4 are
curves showing the relationship between shear modulus and bending rigidity of the core
material, Fig. 5 is an enlarged sectional view of the core material, Fig. 6 is a front view of the core
material, Fig. 7 FIG. 1 is a cross-sectional view showing a part of a flat type speaker diaphragm
according to the present invention, wherein 2 indicates a skin material, 3 indicates a core
material, and 4 indicates a through hole.
DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a diaphragm for a
flat loudspeaker. The existing speaker is a cone type speaker in which a cone type diaphragm as
shown in FIG. 1 is incorporated in a field section not shown. Since the front surface of the
diaphragm is concaved as apparent from the cause of this cone-shaped Souveni force, it has the
disadvantage that a one-thousand-eye vision phenomenon occurs to disturb the frequency
characteristics. Flat loudspeakers have come in the limelight as Svica to overcome this drawback.
Although this half-sided spearing force has an excellent feature of eliminating the abovementioned drawbacks, and a large number of loudspeakers themselves, the diaphragm used in
this loudspeaker has a cone shape. A material with a large flexural rigidity is required as
compared with the case of {circle over (4)} / {circle over (4)} / 7 / {circle over (2)}. FIG. 2 is a
curve ? ? showing the relationship between the half apex angle ? and the stagnation t of the
diaphragm and the resonance frequency f1 generating the first node circular mode in the cone
type diaphragm S shown in FIG. , This relationship is the effective radius R-10 bacteria, specific
elastic modulus E / P = 4 (Km / sec) 2 (where E: Young's modulus, P: density) voice plate coil
mass or negligible voice coil It was adjusted using a speaker mounted. The resonance frequency
f1 is considered to be the limit of the piston movement area of the diaphragm, and the higher
this fl, the more faithful the speaker can be vibrated. In an actual speaker rash, the resonance
frequency f1 is about 70 to 90% of the value of FIG. 2 in the form of a voice coil, an edge or the
like. Here, if FIG. 2 is considered, if the half apex angle ? is small, the diaphragm itself is thin
and bending rigidity D (due to the addition of rigidity resulting from the shape depending on the
apex angle even if D-1 ? 1 is small) The resonance frequency f1 is also high (although it
becomes clear that as the half apex angle ? becomes thicker (when the flat angle approaches ifl,
vibration @ 1 ? larger bending stiffness is required). Therefore, flat 1 il 18 !! In a speaker,
extremely high bending rigidity is required, but as a structure capable of increasing the bending
rigidity, a multilayer formed by laminating several sheets of materials, as well known, as well as
increasing the thickness t Structure exists. The present invention is to provide a flat type speaker
diaphragm having such a multilayer structure. First of all j! The multilayer structure will be
described with reference to FIG. The deflection black of the iron beam 111 when the pile weight
W is added to the multi-dot structure beam 11) as shown in FIG. 1 ml is expressed by the sum of
the bending deformation a1 and the shearing deformation. For the upper bending deformation
J1, ? surface material (2112) acts as shear against the shear deformation 82; the core material
(31 acts as soil.
In the case of simple support, as shown in the figure, in the case of simple support, i3a + = ? иии
(1) 24t + tk + b, where j: length of beam pile thickness of te surface material (2) t: of beam (1) 11:
Thickness of the surface layer: Young's ridge 4b: Width of the beam field is determined. On the
other hand, the shear deformation a2 of the core material (3) is j?2 = ? ииииииииииииииииииииииииииииии (212tx
02b where t2: core material (3 + thickness G 2: core material (3 Given. That is, since the
deflection ? of the multilayer structure beam 111 is the sum of the bending deformation ?1
and the shearing deformation a2, it can be obtained from the above (11 ? and (21). On the other
hand, the deflection ?0 of the single-layered beam can be determined by l?0-? ... 1318 bD.
The relationship between the core material (the thickness t 2 of 31 and the thickness t 1 of the
surface material ? J is usually 1+ ((11 The deflection an of the structural beam is approximately
equal. According to (5), the bending stiffness is 1 + Ga72t + t2t2D ? ? (4) 24E + t + t2 +
2021??t, 2 from the formula 121.131. When the shear modulus G2 of the core material (3) is
large, the bending rigidity is Ds-R + t + t "(5). Equation (5) corresponds to the bending rigidity of
the surface material 12+ of the multi-layered beam. -1, the bending rigidity also decreases as the
shear modulus G2 of the core material 2 decreases. In FIG. 4, the thickness t2 of the core
material (3) is obtained by using the multi-layer structure beam 111 of length t = 1 U1 in which
the core material (3) is held by the surface material made of aluminum of thickness $ 1 = 50
voices. The result of having made the relationship between the bending rigidity at the time of
changing, and the shear modulus G2 of core material T31 m- shows the result. As apparent from
the figure (in the case of a multi-layered structure, it is desirable that the core material 31 has a
thickness t2 as thick and large as possible. Also, if the thickness t2 of the core material 13+ is
small even if the shear modulus 02 of the core material i3 + is the same, the surface material (the
flexural rigidity Di2 of the multi-layer structure is determined in addition to the bending stiffness
of the two rods or the core When it is intended to further increase the bending rigidity by
increasing the thickness t2 of the material port), the shear rigidity of the core material (3) is
insufficient compared to the bending rigidity of the surface material + 21 itself, and the bending
of the multilayer structure The stiffness is considerably lower than the bending stiffness of the
skin (2) itself. On the other hand, the weight of the diaphragm for the speaker is required to have
a low density as the core material 13+ in order to directly affect the performance 4A of the
speaker. The general shear modulus G2 has a relationship of decreasing the density or reducing
the stiffness, and the thickness t2 of the core material 131 is increased (the density of the core
material 131 is decreased to decrease the shear modulus G2 accordingly. ) Cause deterioration of
bending stiffness.
From the above, it can be seen that the characteristics of the core material (3) play an essential
role in giving a large bending stiffness to the diaphragm for flat-panel speaker having a
multilayer structure. a) Usually, as the core material of the multilayer structure, a foamed plastic
such as styrene 7 or urethane is used. This foamed plastic is characterized by low density or lack
of rigidity, and it is difficult to obtain great bending rigidity. A metal material can be considered
as a material having a large rigidity, but it can not be used directly as a core material + 31 having
a large density. However, by making it porous, a low density and high rigidity material can be
obtained. For example, a metal porous structure produced by the method disclosed in Japanese
Patent Publication No. 4710524 can be produced as shown in FIG. 5 (it has a high porosity and
thus a high strength three-way network structure, Cone-type loudspeakers using the. This metal
porous structure receives concentrated stress in part because it has all (differently, almost the
same frame structure or regular three-dimensional connection) with the sintered porous body,
felt metal, etc. No matter (no significant high porosity can be maintained despite the high
strength. Now, as described above, if the density is reduced to increase the density t2 of the core
material 131, the shear modulus G2 of the core material decreases, but in the experimental
measurement, the pores of the 8-metal porous structure And the shear modulus of elasticity of
the substrate of the porous structure is Go, the shear modulus of elasticity G2 is as follows: at = K
(1-i) nno--f5, K: processing at the time of production The relationship of the coefficient r + '2
which is exacerbated depending on the conditions and the material is dropped. In the equation
(5), the decrease in shear elasticity * G2 is remarkable because (1-?) n (1). -In a multi-layer
structure, the stiffness for shear tC should be large with respect to the bending direction of the
plate. As shown in FIG. 6tC, it is possible to increase the stagnation t2 of the core material +31 by
the amount of the through holes ial 141. Assuming that the shear modulus G2 of the core
material (3) in this case is averaged as a whole, when the open area ratio of the through hole
141t4 + is P, it decreases by (1-P) times. However, when the through hole (4 ha 4) is not made,
the density is i-P) 9 times to obtain the same thickness t2 and weight as the core material (3)
with the above hole forming (41 (2)- You have to reduce it. Therefore, the shear modulus G2 is
sharply reduced to (+ -p) times from (5) equation. That is, it is possible to increase the shear
elastic modulus G2 in the bending direction of the plate of the core member +31 by making a
large number of through holes (four holes 4I).
One embodiment of the present invention is shown in FIG. In the same figure, the core material +
31 is made of a nickel ternary reticulated structure having a feces of 6 to 97 v # and a thickness
t 2 of 5 mz, and the diameter of the core material + 31 is about 50%. 1011 III voice through
holes 14 + + и и и are pierced. A skin material made of an aluminum thin plate having a thickness t
1 of 5 DPI 11 which blocks the through holes of the core material (3) and blocks the flow of
nitrogen gas on the front and back sides of the core material (3). ]) (2) is stuck. In addition, one
side of the shape 1 has a square shape of 24 countries. Hydraulic power plate Iii] As shown in
the above description, the diaphragm for circulation Sbi is made of a low-density, high-rigidity
metal porous structure as a material, which has a large number of through-holes as a core
material. Therefore, the conditions required for the flat speaker diaphragm can be satisfied, and
the piston movement area can be further expanded. ??
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