U.S. patent number 3,803,547 [Application Number 05/245,921] was granted by the patent office on 1974-04-09 for electrodynamic transducer for low frequency broad band underwater use.
This patent grant is currently assigned to Massa Division, Dynamics Corporation of America. Invention is credited to Frank Massa.
United States Patent |
3,803,547 |
Massa |
April 9, 1974 |
ELECTRODYNAMIC TRANSDUCER FOR LOW FREQUENCY BROAD BAND UNDERWATER
USE
Abstract
An underwater, low frequency, high power transducer operates at
much greater efficiencies than heretofore possible due to special
relationships between a diaphragm mass and area. The data relating
to the relationship are summarized by the graphs of FIGS. 3 and 4.
The transducer structure includes a tubular housing having a
diaphragm at either end. The internal pressure on the inside
surface of the diaphragms is equalized to the external hydrostatic
pressure in the water at the depth of operation.
Inventors: |
Massa; Frank (Cohasset,
MA) |
Assignee: |
Massa Division, Dynamics
Corporation of America (Hingham, MA)
|
Family
ID: |
22928642 |
Appl.
No.: |
05/245,921 |
Filed: |
April 20, 1972 |
Current U.S.
Class: |
367/175 |
Current CPC
Class: |
G01S
1/72 (20130101) |
Current International
Class: |
G01S
1/00 (20060101); G01S 1/72 (20060101); H04b
013/00 () |
Field of
Search: |
;340/8,9,11,12,14
;181/5A |
References Cited
[Referenced By]
U.S. Patent Documents
Other References
applied Acoustics, Olson and Massa, Second Ed. 1939, Blakiston's
Son & Co., Philadelphia, Pa., Sections 2.10, 7.3,
8.12..
|
Primary Examiner: Borchelt; Benjamin A.
Assistant Examiner: Tudor; H. J.
Claims
1. An electrodynamic transducer for generating uniform acoustic
power under water throughout the lower portion of the audible
frequency spectrum down to the region in the vicinity of 100 Hz,
said transducer comprising magnetic structure means defining a
circular air gap, at least one vibratile diaphragm having a
radiating face approximating a circular piston, flexible suspension
means associated therewith, a coil of insulated electrical
conductor wound and consolidated into a rigid cylindrical shell
supported by one side of said vibratile diaphragm, the mass in
grams of said conductor being greater than approximately twice the
value of the square of the diameter in inches of said circular
piston, the longitudinal axis of said coil being in alignment with
the normal axis perpendicular to the radiating face of said
vibratile diaphragm, frame means rigidly attached to said magnetic
structure means, means for attaching said flexible suspension means
to said frame means with said vibratile diaphragm being supported
by said flexible suspension means in mechanical alignment with the
coil concentrically positioned within said circular air gap, and
waterproof housing means enclosing said air gap and said coil means
together with said one side of said vibratile diaphragm.
2. The invention in claim 1 wherein the diameter of said circular
piston
3. The invention in claim 1 wherein said waterproof housing
includes a
4. An electrodynamic transducer for generating acoustic power under
water throughout substantially all of the lower portion of the
audible frequency spectrum, said transducer comprising a magnetic
structure including a pair of air gaps with one air gap located on
each opposite end of a common axis within said magnetic structure,
a pair of vibratile diaphragm assembly means, each of said
vibratile diaphragm assembly means being associated with a
corresponding one of said air gaps and comprising a rigid piston
portion surrounded by a flexible suspension means, drive coil means
of insulated wire attached to said piston portion on each of said
diaphragms, the mass in grams of each of said drive coil means
being greater than approximately twice the value of the square of
the diameter in inches of the piston portion of the attached
diaphragm, each of said drive coils being supported in an operable
position within one of said air gaps, and waterproof housing means
including a flexible wall portion defining a sealed air volume for
enclosing said magnetic structure and drive coil means, said
vibratile diaphragm assemblies being sealed to said housing means
by said flexible suspension means to provide a completely sealed
air volume enclosure for said magnetic structure and diaphragm
assembly means, said sealed air volume including communication
means extending between said enclosed air volume and the internal
enclosed surfaces of said
5. The invention in claim 4 and a rigid covering surrounding the
outer surface of said flexible wall portion, said rigid covering
having an opening therein for exposing said flexible wall to
ambient external
6. The invention in claim 4 further characterized in that said
piston portions of said vibratile diaphragms have diameters within
the
7. An electrodynamic transducer for operating under water
comprising an elongated magnetic circuit having an axial core, an
annular air gap located at each opposite end of said axial core,
two identical vibratile diaphragm assemblies, each diaphragm
assembly having an internal and an external side, each diaphragm
assembly further comprising a rigid piston portion surrounded by a
peripheral waterproof flexible suspension means, and each diaphragm
assembly including a drive coil of insulated wire rigidly attached
to the center internal side of each vibratile diaphragm, the mass
in grams of each of said drive coils being greater than
approximately twice the value of the square of the diameter of the
piston portion of said diaphragm assembly, a structural support
means rigidly attached to each end of said elongated magnetic
circuit, said waterproof flexible suspension means operably sealing
the periphery of each vibratile diaphragm to each of said
structural support means with the associated coil of each diaphragm
operably located in one of said annular air gaps, a waterproof
housing sealingly enclosing said magnetic structure and the
internal sides of said vibratile diaphragm assemblies whereby a
waterproof enclosure is achieved for the transducer assembly, and
pressure compensating means including an air volume on the inside
of said waterproof housing with communicating passageways extending
from said air
8. The invention in claim 7 wherein the diameter of the active
piston portions of said vibratile diaphragm assemblies lie in the
range extending
9. The invention in claim 7 wherein said waterproof housing has a
flexible tubular wall, a rigid tubular housing surrounding said
flexible tubular housing, said rigid tubular housing including an
opening for enabling the flow of water from the outside surface of
said rigid housing to the inside surface of said rigid housing,
thereby equalizing ambient pressures inside
10. The invention in claim 9 wherein the diameter of the active
piston portions of said vibratile diaphragms lies within the
approximate range of
11. The invention in claim 7 wherein the diameters of the piston
portions of said vibratile diaphragm assemblies lie within the
approximate range of 4 to 12 inches and the mass in grams of each
of said drive coils is more than approximately twice the value of
the square of the diameter in inches
12. A dual electrodynamic transducer comprising an elongated
cylindrical housing sealed on both ends by a diaphragm assembly
having a frustoconical section filled with a rigidifying substance
and having a coil at least partially surrounding the truncated apex
of said frustroconical section, the mass of said coil comprising an
electric conductor having a mass in grams greater than
approximately twice the value of the square of the diameter in
inches of said rigidified portion of said diaphragm.
Description
This invention relates to underwater transducers, and more
particularly to underwater transducers capable of generating
uniform acoustic power over a large portion of the lower audible
frequency spectrum.
The invention is specifically concerned with the design of a
compact transducer in which the diameter of the vibrating surface
is in the range between a few inches and one foot and which is
capable of generating acoustic power levels in excess of 1 watt
over a broad portion of the lower audible frequency spectrum, down
to frequencies in the order of 100 Hz or less.
In order to achieve a uniform transmitting response characteristic
over the entire lower audible frequency range, a rigid vibratile
diaphragm is flexibly mounted by a suspension system having
sufficient compliance to resonate the vibrating system below the
lowest frequency to be reproduced. The mechanical impedance of the
vibrating system is mass controlled over the entire frequency
region requiring flat response. The vibratile piston will be driven
by electrodynamic forces generated in an attached coil of wire
which is suspended in a magnetic field. This strucuture is similar
to conventional dynamic speakers for home sound reproducing
equipment.
Previous designs of electrodynamic underwater transducers have
failed to provide significant acoustic power output levels. The
acoustic power output has generally been limited to a small
fraction of a watt. This low power limitation was inherent in
previous designs because the vibratile diaphragm was either too
small (generally only 2 or 3 inches diameter) and therefore
incapable of making the large excursions necessary to generate
power levels in the order of 1 watt or greater for frequencies in
the neighborhood of 100 Hz; or, for larger size diaphragms, the
efficiency was so low (in the neighborhood of 0.1 percent) that the
electrical power loss in the voice coil would burn it out, if
driven at the power levels required to produce acoustic power
levels in the order of 1 watt or greater in the 100 Hz region.
The primary object of this invention is to overcome the inherent
limitations in previously designed electrodynamic transducers for
underwater generation of sound.
Another object of this invention is to provide electrodynamic
transducers employing a vibratile piston several inches in
diameter, capable of a wide range, uniform response, over the lower
audible frequency range, down to the region of 100 Hz or less and
having an efficiency in excess of 1 percent.
An additional object of this invention is to provide electrodynamic
transducers for underwater use, capable of generating acoustic
power levels in excess of 1 watt in the lower audible frequency
region down to the vicinity of 100 Hz or less.
A still further object of this invention is to provide a compact
electrodynamic transducer design in which two vibratile pistons are
mounted to radiate from opposite ends of the axis of the structure,
whereby each piston effectively becomes loaded as if it were
mounted in an infinite baffle and, as such, each of the two pistons
individually generates approximately twice the acoustic power for a
given displacement that would result for the same piston operating
singly and mounted on one face of an enclosing housing.
Another object of this invention is to specify the minimum
relationships that must be satisfied between the mass of the voice
coil and diameter of the vibratile piston in order that the
efficiency of the transducer shall exceed 1 percent.
These and other objects, features and advantages of the invention
will become more apparent from a study of the following description
when taken in conjunction with the drawings, wherein:
FIG. 1 is an end view of a transducer incorporating one
illustrative embodiment of my invention;
FIG. 2 is a cross-sectional view taken along the line 2--2 of FIG.
1;
FIG. 3 is a chart showing the relationship between the coil mass
and transducer efficiency for pistons of various sizes; and
FIG. 4 is a chart showing the relationship between acoustic power
output and frequency for diaphragms of various diameters vibrating
at constant amplitude.
In the figures, the reference character 1 identifies a cylindrical
core of magnetic conducting material which is accurately machined,
at each end, to define the inside diameter of an annular air gap at
each end of the core. A hollow cylindrical permanent magnet 2 is
provided with end plates 3 and 3A of magnetic conducting material,
such as soft iron. Each of the end plates has a hole machined
through its center to define the outside diameter of the annular
air gaps as illustrated in FIG. 2. The end plates 3 and 3A are
provided with brass collars 4 and 4A which are attached by means of
the screws 5. A clearance hole is machined through each collar 4
and 4A, so that the machined ends of the core piece 1 can be held
in concentric alignment with the holes in the end plates 3 and 3A,
to provide a uniform concentric air gap at each end of the magnetic
assembly as illustrated in FIG. 2. A convenient means for insuring
that the holes in the plate members 3 and 3A are concentric with
the holes in the collars 4 and 4A is to mahcine the final hole
sizes after attaching the collars 4 and 4A to the end plates 3 and
3A. The end plates 3 and 3A may be held to the ends of the magnet 2
by means of a suitable cement, such as epoxy. After assembling the
magnetic structure, I prefer to fill the space between the core 1
and the permanent magnet 2 with a potting compound 6 which may be
poured into the space through a small hole through either the wall
of the magnet or the surface of one of the end plates 3.
At each end of the magnetic structure is attached a vibratile
diaphragm assembly, one of which comprises a voice coil 7 wound on
a tubular coil form 8. The coil form 8 is bonded to a mating
surface 9 provided at the base of the diaphragm 10, as illustrated.
The voice coil 7 comprises several layers of insulated wire wound
over the coil form 8 and held together as a composite rigid
assembly by a suitable cement, such as epoxy, as is well known in
the art of loud speaker construction. The diaphragm structure
comprises a truncated conically shaped waterproof diaphragm 10
which includes a corrugation 11 formed near the outer periphery to
provide a flexible suspension means for enabling relatively large
excursions of the diaphragm. A suitable material for the diaphragm
structure 10 would be stainless steel which is rugged and resistive
to the corrosive action of the underwater environment. The outer
flat peripheral portion of the diaphragm 10 is nested within a
recessed cavity 12 machined into the face of the structural frame
member 13. To provide added stiffness for forming a piston portion
at the central vibratile portion of the diaphragm structure, the
conical cavity portion of diaphragm 10 is filled with a rigid
potting compound 14, such as epoxy. The diaphragm 10 with its
attached voice coil assembly 7 and 8 is mounted on the structural
support member 13 by using proper locating fixtures to insure that
the voice coil is located exactly along the center line of the
structure. Two insulated conductors 15 and 16, which provide
electrical connection to the coil 7, pass through a hole provided
in structural member 13, as illustrated.
The diaphragm assembly mounted at the opposite end of the magnetic
structure is identical to the diaphragm assembly just described. It
comprises voice coil 7A and coil form 8A attached to diaphragm 10A,
which is attached to frame member 13A similar to the previously
described assembly. Frame member 13A includes a counterbored hole,
through its face, to enable a watertight assembly of a waterproof
cable 17 by means of the gland nut 18, washer 19, and rubber
grommet 20, as shown. The conductors 15, 16, 15A and 16A, from the
voice coils 7 and 7A are connected together and to the conductors
in cable 17 in such phase that an electrical signal supplied to the
cable will cause both diaphragms 10 and 10A to move together,
simultaneously away or toward the center of the core piece 1, in
accordance with the polarity of the a-c signals supplied through
the cable 17.
The diaphragm assemblies 10 and 10A, together with their support
members 13 and 13A, are attached to the end plates 3 and 3A and are
held in place by the screws 21, as illustrated. At this point in
the assembly, the structure comprises a pair of vibratile
diaphragms assembled to opposite ends of a magnetic structure. They
are capable of being driven by mechanical forces generated within
their respective voice coils which are suspended in annular air
gaps provided on opposite ends of a common magnetic circuit.
After the electrical connections are made between the conductors
15, 16, 15A, 16A and the conductors from the cable 17, a rubber
boot 22 is stretched over and attached to the outer periphery of
the structure 13 to provide a watertight seal to the internal
transducer structure. The rubber boot 22 is sealed to the edge
surfaces of members 13 and 13A by circumferential pressure applied
by the metal bands 23, as illustrated. A sealed air volume 24
inside the flexible rubber boot 22 communicates with the clearance
spaces 25 and 25A, as shown in FIG. 2. When the transducer is
lowered in water, the flexible boot 22 compresses air volume 24 to
equalize the internal pressure to the external water pressure. A
rigid cylindrical sleeve 26 is attached to the outer peripheral
ends of structural members 13 and 13A by means of the screws 27 to
complete the assembly. A few small holes 28 through the wall of the
cylindrical tubing 26 permit the entrance of water in the space 29
when the transducer is immersed in the sea. The purpose for
providing the rigid sleeve 26 to enclose the rubber boot is to
prevent the unprotected exposure to the sea of the low impedance
pressure release surface, represented by the air backed rubber boot
22, which would otherwise reduce the efficiency of radiation of
sound from the transducer.
The invention is concerned with the configuration of the dual
diaphragm system which, when operating together, effectively
performs as if each diaphragm was separately mounted in an infinite
baffle, which results in an improved radiation resistance load on
each diaphragm. In other words, by having the dual diaphragms
operate as described, each diaphragm will individually have
approximately twice the radiation resistance on its surface, as
compared to the case where only a single diaphragm is operating
from one end of a conventional magnetic structure. This means that
the use of two diaphragms, with each diaphragm vibrating at the
same amplitude, will generate approximately four times the acoustic
power that would be generated by one diaphragm operating
separately.
The basic invention resides primarily in the relationships that I
have found necessary to be satisfied between the mass of the voice
coil and the size of the diaphragm, in order to achieve the greatly
improved efficiency and power generating capability which I have
achieved over the prior art electrodynamic transducers designed to
operate over a broad frequency range, at the lower region of the
audible frequency spectrum, down to frequencies in the vicinity of
100 Hz. Electrodynamic transducers which have heretofore been
designed for underwater use have efficiencies in the vicinity of
0.1 percent. Because of such low efficiencies, the acoustic power
output is limited to a small fraction of a watt since there is a
tremendous temperature rise in the voice coil, which occurs due to
the high losses. By applying the teachings disclosed in this
invention, I am able to very materially increase the efficiency and
also the power output capability of an electrodynamic transducer
operating under water over the lower audible frequency range.
In order to investigate the efficiency and power generating
capability of the transducer structure which has been described,
each diaphragm may be considered as being effectively mounted in an
infinite baffle. Since the diameter of the diaphragm is small as
compared to the wave length of sound at the low frequencies of
interest, the dual diaphragm structure will radiate sound in an
omnidirectional pattern. In order to support the conditions which
will be claimed for achieving the improvements in electrodynamic
low frequency transducers as stated (namely: the transducer is
capable of generating acoustic power levels greater than 1 watt,
and the efficiency of the inventive transducer is greater than 1
percent as compared to the prior art designs having efficiencies in
the vicinity of 0.1 percent) a brief mathematical analysis will be
presented together with specific numerical data to permit the
selection of the necessary parameters to achieve the teachings of
this invention.
It can be shown from fundamental principles such as presented in
section 2.10 of the book by Olson and Massa, entitled Applied
Acoustics, second edition, P. Blakiston's Son & Co.,
Philadelphia, 1939, that the acoustic impedance loading on the
surface of a small piston mounted in an infinite baffle is given by
the expression
z = .rho.c k.sup.2 r.sup.2 /2 + j8R.omega..rho./3.pi. (1)
where:
z = specific radiation impedance in mechanical ohms/cm.sup.2
.rho. = density of the medium in gms/cm.sup.3
c = velocity of sound in the medium in cm/sec
k = 2.pi./.lambda.
.lambda. = wavelength in cm = c/f
f = frequency in Hz
R = radius of piston in cm.
The total radiation impedance on the surface of a piston in an
infinite baffle radiating low frequencies in water can be derived
from Equation (1) and is given by
Z.sub.M = 1.04 .times. 10.sup..sup.-3 D.sup.4 f.sup.2 + j
30.4D.sup.3 f mechanical ohms (2)
from which,
R.sub.M = 1.04 .times. 10.sup..sup.-3 D.sup.4 f.sup.2 mech. ohms
(3) X.sub.M = 30.4 D.sup.3 (4) ech. ohms
where:
D = piston diameter in inches
f = frequency in Hz.
Since the reactance X.sub.M in Equation (4) is equal to
.omega.M.sub.W, where M.sub.W is the magnitude of the water load on
the surface of the vibrating piston, it follows that
M.sub.W = 4.85 D.sup.3 grams. (5)
The motional impedance, which appears in series with the electrical
impedance of the voice in an electrodynamic transducer, is equal
to
Z.sub.EM = B.sup.2 L.sup.2 .times. 10.sup..sup.-9 / R.sub.M +
j.omega.M.sub.o ohm (6)
where:
B = air gap flux density in gauss
L = length of conductor in voice coil, in cm
R.sub.M = radiation resistance in mech. ohms
M.sub.o = total mass of vibrating system in grams.
The largest portion of M.sub.o is the water load which is given by
Equation (5). It is possible to keep the total mass of the piston
plus voice coil to within about 50 percent of the water load mass;
therefore, it will be assumed that M.sub.o is equal to about 1-1/2
times the value of M.sub.W in Equation (5). Therefore, for purposes
of this analysis,
M.sub.o = 7.5D.sup.3 grams. (7)
Substituting the values of R.sub.M from Equation (3) and M.sub.o
from Equation (7) into Equation (6), the motional impedance
becomes
Z.sub.EM = B.sup.2 L.sup.2 .times. 10.sup.-.sup.9 /1.04 .times.
10.sup..sup.-3 D.sup.4 f.sup.2 + j47D.sup.3 f. (8)
By multiplying the numerator and denominator by the conjugate of
the denominator, the expression for the motional impedance
becomes
Z.sub.EM = B.sup.2 L.sup.2 .times. 10.sup..sup.-9 (1.04 .times.
10.sup..sup.-3 Df - j47)/D f (1.08 .times. 10.sup..sup.-6 D.sup.2
f.sup.2 + 2200). (9)
For the purposes of the transducer design covered by this
invention, the diameter of the diaphragm is always less than
one-fourth wavelength of the sound being generated in the water;
therefore, the first term inside the bottom parantheses becomes
negligibly small and expression for motional impedance reduces
to
Z.sub.EM = B.sup.2 L.sup.2 .times. 10.sup..sup.-9 (1.04 .times.
10.sup..sup.-3 Df - j47/2200 D.sup.3 f (10)
from which the real part represents the motional resistance, which
is equal to
R.sub.EM = 4.8 .times. 10.sup..sup.-16 B.sup.2 L.sup.2 /D.sup.2
ohm. (11)
Since the motional resistance in Equation (11) appears in series
with the resistance of the voice coil, it follows that the
efficiency of the electrodynamically driven piston mounted in an
infinite baffle is given by
Eff. = R.sub.EM /R.sub.EM + R.sub.E .times. 100 percent (12)
where:
R.sub.E = voice coil resistance in ohms.
For a copper conductor of length L cms and mass M.sub.c grams,
R.sub.E = 15,2 .times. 10.sup..sup.-6 L.sup.2 /M.sub.c ohms.
(13)
Substituting Equation (13) and Equation (11) into Equation (12),
the efficiency becomes
Eff. = 3.15 .times. 10.sup..sup.-11 B.sup.2 M.sub.c /3.15 .times.
10.sup..sup.-11 B.sup.2 M.sub.c +D.sup.2 .times. 100 percent.
(14)
To give a physical interpretation of the analytical conclusions
developed above and to present specific design data that can be
used by a transducer engineer to design low frequency underwater
wide range transducers with efficiencies greater than 1 percent, in
accordance with the teachings of the invention, a family of curves
have been computed from Equation (14). These curves show the mass
of copper conductor required in the voice coil design of an
electrodynamic transducer as a function of efficiency for various
pistons ranging from 2 to 10 inches in diameter. The data are shown
in FIG. 3 and are based on an assumed value of air gap flux density
equal to 12,000 gausses. This value of flux density is a reasonable
maximum that can be obtained with the best grades of Alnico magnets
that are commercially available. For lower values of flux density,
the voice coil mass required for a fixed efficiency and piston
diameter will increase in inverse proportion to the square of the
flux density.
Using the assumed maximum value of 12,000 gausses in the air gap,
it can be seen from the data in FIG. 3 that the requirement to be
met for achieving a transducer efficiency greater than 1 percent
is
M.sub.c >2.2D.sup.2 grams. (15)
For example, if a 7 inches diameter piston is chosen for the
transducer diaphragm, it will be necessary to design a voice coil
employing more than approximately 100 grams of copper to achieve an
efficiency greater than 1 percent. If the flux density is reduced
from the 12,000 gauss assumed value, then the voice coil has to
employ a still greater quantity of copper.
It would seem from an inspection of the data in FIG. 3 that all
that is necessary to design a high efficiency transducer with a
relatively lightweight coil and corresponding lightweight magnetic
structure is to use a small diameter piston. For example, a 2
inches diameter piston requires only 9 grams of copper in the drive
coil to achieve an efficiency of 1 percent. This is correct as far
as efficiency is concerned; however, a 2 inches diameter piston
will not be able to generate much power at the lower audible
frequencies due to the limitation in maximum amplitude of vibration
which is imposed by the magnetic structure. In order for the
transducer to generate an acoustic power level of at least 1 watt
at 100 Hz, it will be necessary for the piston diameter to be not
less than the minimum value required to prevent amplitudes of
vibration from exceeding the linear range provided in the air gap
design.
The acoustic power generated by a vibrating piston can be
determined by multiplying Equation (3) by the square of the piston
velocity. The acoustic power output from the piston is
P.sub.A = .omega..sup.2 A.sup.2 .times. 1.04 .times. 10.sup..sup.-3
D.sup.4 f.sup.2 .times. 10.sup..sup.-7 watts (16)
where:
A = piston amplitude in cm.
By combining terms, Equation (16) may be rewritten as
P.sub.A = 2.6d.sup.2 D.sup.4 f.sup.4 .times. 10.sup..sup.-14 watts
(17)
where:
d = piston amplitude in mils.
The information represented by Equation (17) was used to produce
the family of curves in FIG. 4 which show the acoustic power output
generated over the frequency range 100 Hz -- 1,000 Hz by various
pistons ranging in diameter from 1 to 10 inches when vibrated at an
r.m.s. amplitude of 10 mils (which is equivalent to a peak-to-peak
amplitude of 28 mils for a sinusoidal vibration). An inspection of
the curves in FIG. 4 show that the 2 inches diameter piston
mentioned earlier can only generate about 10 milliwatts of power at
100 Hz for the assumed 10 mils r.m.s. amplitude. It is also shown
that, for a piston to be able to generate 1 watt acoustic power at
100 Hz at 10 mils r.m.s. amplitude, the piston diameter must be
about 8 inches. If the maximum permissible amplitude were increased
to 20 mils r.m.s. (56 mils peak-to-peak), a 6 inches diameter
piston would be required to generate 1 watt output at 100 Hz. Even
if the requirement is that each diaphragm of the dual structure
shown in FIG. 2 generate only one-half watt each, in order for the
complete transducer to generate 1 watt at 100 Hz, the piston
diameter must be greater than 4 inches if the maximum peak-to-peak
excursion of the voice coil is to be limited to approximate 60
mils, which is a fairly large excursion to accommodate and still
maintain linearity in the transducer.
This invention has disclosed the design of a low frequency,
electrodynamic, underwater transducer capable of greatly exceeding
the efficiency and power generating capabilities of prior art
designs. Specific design data has also been presented showing the
relationships between the magnitudes of the various parameters
which define the basic elements of the vibrating system and the
acoustic performance of the transducer.
Although only a few specific examples have been discussed to
illustrate the teachings of this invention, it is obvious that some
variations may be made in the specified limits chosen to illustrate
the invention, without departing materially from the conclusions
which have been drawn. Other obvious changes in some of the details
which have been mentioned may be made by those skilled in the art
without departing substantially from the teachings of this
invention. Therefore, I desire that my invention shall not be
limited except insofar as is made necessary by the prior art and
that the appended claims be construed to cover all equivalent
structures.
* * * * *