U.S. patent number 3,772,538 [Application Number 05/321,976] was granted by the patent office on 1973-11-13 for center bolt type acoustic transducer.
This patent grant is currently assigned to Du Kane Corporation. Invention is credited to Michael C. Supitilov.
United States Patent |
3,772,538 |
Supitilov |
November 13, 1973 |
CENTER BOLT TYPE ACOUSTIC TRANSDUCER
Abstract
A center bolt type of acoustic transducer has means for mounting
such transducer at the nodal plane. This means includes a flange
integral with a transducer part and rigid clamping rings
cooperating with such flange but acoustically isolated therefrom by
suitable gaskets for support. The nodal plane is located at the
flange.
Inventors: |
Supitilov; Michael C. (St.
Charles, IL) |
Assignee: |
Du Kane Corporation (St.
Charles, IL)
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Family
ID: |
23252867 |
Appl.
No.: |
05/321,976 |
Filed: |
January 8, 1973 |
Related U.S. Patent Documents
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Application
Number |
Filing Date |
Patent Number |
Issue Date |
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199892 |
Nov 18, 1971 |
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034220 |
May 4, 1970 |
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Current U.S.
Class: |
310/325 |
Current CPC
Class: |
B06B
1/0618 (20130101) |
Current International
Class: |
B06B
1/06 (20060101); H04r 017/00 () |
Field of
Search: |
;310/8.1,8.2,8.3,8.7,9.1-9.4 |
References Cited
[Referenced By]
U.S. Patent Documents
Primary Examiner: Miller; J. D.
Assistant Examiner: Budd; Mark O.
Claims
I claim:
1. An ultrasonic transducer comprising two piezo-electric ceramic
discs with a high potential electrode therebetween arranged to form
a stack, said ceramic discs having flat surfaces, electrically
grounded front and rear acoustic resonators axially aligned with
said stack and having conforming shapes and at least equal areas
cooperating with the flat disc surfaces, axially disposed bolt
means for retaining as an assembly said resonators and said stack
under predetermined compression, said front resonator having its
rear-end portion shaped so that sections transverse to the
resonator axis are circular, and the front end thereof being
adapted to feed ultrasonic energy for work, said rearend portion
having an integral outwardly extending uniformly thick support
flange having a thickness along the front resonator length which is
small in terms of operating wave length but thick enough to be
strong, said transducer having a nodal plane at the flange; mating
rigid rings disposed at opposite sides of said flange, a readily
compressible heat resistant gasket ring at each side of said
support flange, each said gasket ring contacting substantially all
of the opposed surfaces of said flange sides and portions of said
rigid rings and also contacting outer surfaces of the transducer's
said assembly parts adjacent the flange, means for supporting said
rigid rings in predetermined spaced relationship, said rigid rings
forming part of a mount for the entire transducer assembly, said
rigid rings having sufficient clearance with respect to the body of
said transducer's said assembly parts to accommodate limited
vibration isolation at said gasket rings consistent with mounting
rigidity between the transducer assembly and said rigid rings, the
generally distributed compression of gasket rings between gasket
compressing surfaces preventing the formation of destructive
localized hot spots in said gasket material; said transducer having
minimum interfaces to minimize interface losses and the flange
transmitting directly to said front resonator load pressure without
significantly affecting the nature or distribution of the
predetermined compression force on the ceramics and without
increasing the bolt tension significantly.
2. The construction according to claim 1 wherein said flange is
located forwardly of the rear end face of the front resonator so
that said two gasket rings may be disposed on opposite sides of the
flange about the rear end portion of said front resonator.
3. The construction according to claim 1 wherein at least one of
the surfaces against which a gasket is compressed has relatively
small irregularities for frictionally locking the adjacent gasket
material against relative movement whereby a gasket is prevented
from moving with respect to the transducer about the axis of said
transducer assembly.
4. The construction according to claim 1 wherein said flange is
located so that one sidewall thereof forms an extension of the rear
end of said front resonator with one gasket overlying the adjacent
end of a ceramic.
5. The construction according to claim 1 wherein said front
resonator tapers from its flanged rear end portion with said
resonator cross sectional area decreasing as the front end is
approached, said front resonator having a length somewhat in excess
of one-quarter wave length, said front end of said front resonator
providing a mechanical advantage in amplitude increase whereby a
compact transducer structure is provided.
Description
This invention relates to a center bolt type of acoustic transducer
employing flat piezo-electric ceramic plates. A transducer
embodying the present invention is capable of operation at moderate
levels of power and is sufficiently versatile to function
efficiently as a general tool for a variety of work.
The above type of transducer generally consists of a so-called rear
slug, usually of metal, and an axially aligned front slug (or horn)
between which are disposed a high potential electrode and at least
two piezo-electric ceramic plates, hereinafter sometimes referred
to merely as "ceramics," but understood to have piezo properties.
The assembly is maintained in preset compression by an axial bolt.
Such an assembly is generally operated at a suitable frequency (as
an example, about 20,000 Hz) for accomplishing various
objectives.
Transducers of this general type have problems in connection with
interfaces between physically separate parts of a transducer and
also in connection with supporting the unit. In addition, such
transducers are not susceptible to adaption for various jobs
requiring tool change without factory adjustment or redesign. In
many instances prior transducers are not adaptable for operating in
parallel as part of a battery of transducers without substantial
spacing between adjacent transducers. Such spacing is due to
mounting requirements of each transducer.
An additional disadvantage of some prior transducers is the
inability to change the number of the vibration transmitting
half-wave lengths at the front slug (or horn) as may be necessary
to apply acoustic energy to a desired work region. A substantial
drawback in prior transducers is the number of separate parts (and
thus the number of interfaces) required in a transducer unit
maintained in preset compression by the axial bolt means. This last
named drawback may result in reduced efficiency and definitely in
increased manufacturing cost. Opposed faces of separate physical
parts of a transducer unit, maintained in compression, must be
finished to about one ten thousandth of an inch and involves
painstaking and precise preparations of opposed faces.
In many transducers, the mounting of the entire unit on a
stationary support results in feedback of static support force to
piezo ceramic static compression force and thus affects preset
static ceramic compression.
A transducer embodying the present invention has definite
advantages over prior transducers. The new transducer has minimum
number of interfaces requiring preparation of opposing surfaces;
the entire transducer assembly, preset for predetermined piezo
ceramic compression need not be disturbed when making a tool change
at the work end thereof; the stationary transducer support means is
statically independent of static ceramic compression forces; the
new transducer permits close spacing between separate parallel
transducers and thus permits transducers to operate within minimum
space.
A transducer embodying the present invention comprises a high
potential flat electrode plate of substantial thickness having flat
ceramic plates disposed on opposite sides of the electrode. A rear
slug is disposed against one face of a ceramic and a front slug (or
horn as required) is disposed against the outer face of the
remaining ceramic. A bolt extends axially through the assembly and
is pretensioned by internally threaded portions to subject the
ceramics to a predetermined operating compression.
For convenience, round ceramic discs are used. The same circular
configuration is also used for the elements of an assembly. Except
for the ceramics which should not project beyond the metal
portions, the outer diameters of the ceramics, electrode plate and
rear slug may be the same. The front slug (or horn) will have a
circular outer shape, at least at the rear portion thereof. The
outer diameter of the front slug at the rear portion thereof will
be somewhat greater than that of the adjacent ceramic due to the
presence of a mounting flange extending radially from the slug
exterior. Otherwise the forward slug (or horn) will have a shape
and/or dimensions dictated by engineering considerations. The
mounting flange is part of a stationary mount structure.
The mount structure for a transducer provides a highly efficient
and effective support means. The transducer mount is such that the
static weight or load pressure of a transducer unit will not result
in any change of pre-compression upon the ceramics, thus isolating
the static preset force of compression on the ceramics from the
mounting of a transducer with relation to work. The annular support
flange for a transducer projects laterally beyond the remaining
peripheral parts of the transducer. The extent of support flange
projection is quite small so that the entire transducer has minimum
requirements for mounting space.
The new transducer has its vibratory output longitudinally of the
transducer assembly. The nodal plane is normal to the transducer
axis at the annular flange and has minimum vibratory amplitude.
Longitudinally in either direction from the nodal plane the
amplitude of longitudinal vibration increases to a maximum along
the transducer axis at a region one-fourth of a wave length away
from the nodal plane and thereafter decreases further away from the
first nodal plane until one-fourth of a wave length from the
maximum or peak amplitude there is a new nodal plane. As a rule, a
transducer generally extends only for one-fourth wave length to the
non-working rear end thereof. The front (working) portion is
dimensioned to be some desirable number of odd one-fourth wave
lengths from the center of the nodal flange.
In the new transducer, the nodal plane is located near the rear of
the forward slug (or horn). In this new construction, the front
slug (or horn) is always somewhat longer than one-fourth wave
length (or odd multiple thereof).
The location of the nodal plane forwardly of the ceramic assembly
has a number of advantages. The design of the transducer mount
structure is quite flexible and lends itself to accommodating
various shapes of transducer housings. The housing may be designed
to provide protection for high and ground potential leads; to
insure adequate dissipation of heat; to support the housing and
transducer in desired relation to the work; and in general to
isolate the static load on the work from the static load on the
ceramics.
A transducer assembly inherently has interfaces between dissimilar
solid materials having different acoustic impedances. Vibratory
energy travelling along a path through one solid medium and
encountering a different solid medium invariably suffers a
transmission loss in the form of backwardly reflected waves. In a
homogeneous solid medium, the interlinking of crystals makes for
minimum transmission losses. However, where the nature of a solid
medium changes, as between ceramic and metal, or between two
different metals, then the effectiveness of energy transmission
will depend upon the relative complex acoustic impedances of the
materials and how intimately the solid materials on opposite sides
of an interface can be in physical contact with each other. The
smoother and flatter the opposed faces are, the less air space
there will be between the two solids. 100 percent is a theoretical
ideal which cannot be attained. Careful surface preparation can
come close to the ideal so that transmission of wave energy through
an interface may reach a value of the order of about 90 or 95
percent. Grease "couplants" are sometimes used. It is obvious that
successive interfaces in a wave transmission path can rapidly cut
down overall transmission efficiency, especially if the facing
surfaces are not smooth and flat.
A ceramic disc is available with a very thin silver coating on each
face originally put on for "poling" purposes during manufacturing.
The face is usually smooth and true to about a few tenths of a
thousandth of an inch. The bond between silver and ceramic is good
enough so that the silver coating may be retained.
Practical considerations dictate the use of a high potential
electrode having substantial thickness. The new transducer
embodying the present invention has a minimum number of interfaces.
These interfaces are on both sides of each of two ceramic discs.
Having a high potential relatively thick metal electrode disc
minimizes some lead assembly problems for applying potential to the
ceramics.
The new transducer assembly in general includes forward and rear
slugs between which is disposed the ceramic containing portion of
the assembly. This portion comprises two ceramic discs properly
poled and having a common high potential electrode between them.
Axially within the slugs, ceramic discs and intervening electrode
is a bolt for maintaining the transducer assembly at a
predetermined compression. The bolt referred to is frequently
designated as a cap screw, but for convenience, the word bolt will
be used herein.
The rear slug (which may be of a suitable solid) is preferably of
steel or other dense metal and with the ceramics and high potential
electrode extends for somewhat less than one-fourth wave length at
the desired operating frequency. The nodal palne is theoretically
established near the rear end of, but within, the forward slug,
ideally the center plane of flange thickness. It is understood that
the total physical length of the parts will depend on the frequency
at which the transducer is to be operated. In the new transducer,
while structural details are not dependent upon any particular
frequency, where appropriate the specific figures or discussion
will be in connection with a system for operation at or about
twenty thousand cycles per second (20KHz). The ceramics may be
discs having a thickness of the order of about one-fourth inch, the
outer diameter substantially 11/2 inches with an axial hole
therethrough having a diameter of about one-half inch for
accommodating a compression bolt. The rear slug is cylindrical and
has its outer diameter equal to that of the ceramics. The front
slug is of suitable matter, as titanium or high strength aluminum,
and may be cylindrical or, except for the rear portion,
non-cylindrical, depending upon engineering considerations. As is
well known in this art, from the rear face of the forward slug the
forward working slug (or horn) may vary toward the working or tool
end in cross sectional area and shape, as exponential, catenoidal,
linear, etc., horn profiles, all well known and fully set forth in
published literature, to provide desired operating characteristics
at the tool end.
The ceramic material may be anyone of a number of materials well
known in the art and available on the market. Presently, ceramic
materials are of barium titanate, lead zirconate titanate and other
related compounds. These materials are desirable because they can
withstand moderately high temperatures; have suitable electrical
properties; are available at relatively low cost and have
acceptable mechanical properties. As a rule, ceramics can withstand
considerable compression forces but are weak in tension. Thus, any
force tending to bend a ceramic plate (due, for example, to
improper matching of faces of ceramic and metal) will result in
fracture of a ceramic plate.
In considering the assembly of high potential electrode, ceramics
and slugs, maintained in predetermined compression by an axial
bolt, the term rear slug or resonator may be used to describe a
cylindrical member. Forwardly of the ceramic plates, the member may
be designated as a front slug or resonator or horn depending upon
its function. Generally, slug or resonator are frequently used
interchangeably where the member has a generally cylindrical shape
and a constant outer diameter. The same is true of the rear slug or
resonator. However, unlike the rear slug or resonator, the forward
functioning member may not only have a wave transmission function,
but also a wave amplitude function in which case such member is
usually designated as a horn.
Where forwardly of the ceramic array it is necessary to have a long
energy path to the tool tip (as in working inside of long pipes),
additional multiples of half wave may be provided bolted together
to extend the energy conducting path by an integral number of
additional half waves. The tool slug (or horn) will be at the end.
Path extending slugs may be cylindrical with all amplitude
transforming functions concentrated in the end working horn
carrying the tool or there may be impedance transforming sections.
The slugs on both ceramic faces are provided with axial passages or
recesses for accommodating a bolt for maintaining an assembly in
compressed condition.
In accordance with the invention, an improved supporting means at a
nodal plane is provided. The nature and location of means
supporting a transducer assembly is important because this may
represent a drain of acoustic power from the transducer.
The invention will now be described in connection with the drawings
wherein
FIG. 1 is a view in section for the most part with certain parts
being shown in elevation of a transducer unit embodying present
invention, the unit being mounted in a housing, the transducer unit
being provided with a tapering horn, shown in section, and a front
slug, as a modification, shown in dotted lines.
FIG. 2 is a side elevation of a mounting ring for the
transducer.
FIG. 3 is a view on line 3--3 of FIG. 2 showing two mounting rings
for a transducer.
FIG. 4 is an enlarged detail of the mounting rings and gaskets.
FIG. 5 is an elevation of a front horn having a modified gasket
support.
FIG. 6 is an enlarged detail illustrating the modified gasket
support of FIG. 5 in an assembled transducer.
FIG. 7 is a detail of an outwardly tapering horn which may be used
with the new transducer.
FIG. 8 is an exploded view showing a two piece clamping ring for
use with the general horn arrangement illustrated in FIG. 7, the
rings being shown in exaggerated form to illustrate the mechanical
construction.
Referring to the drawings, the transducer includes back or rear
slug 10 having flat end faces 11 and 12. Slug 10 preferably is
cylindrical with axial bore 14 and counter-bore portion 15. The
counter-bore extends from free end face 11 for a part of the slug
length to internal flat annular shoulder 16. The location of
shoulder 16 with respect to the slug length is not critical for
general applications and it may be located about two-thirds of way
between slug end faces 11 and 12, as shown. The longitudinal
location of shoulder 16 will be determined in substantial measure
by acoustic and mechanical considerations including the length of
the compression bolt to be used, its diameter, modulus of
elasticity, strength, etc. The radial dimension of shoulder 16 will
be determined by mechanical engineering requirements including
clearance for the size of the bolt head, or for washer diameters if
used. The diameter of bore 14 will be determined by the diameter of
the bolt shank or for other desired clearances while the outer
diameter of slut 10 will be determined by the outer diameter of the
ceramic discs.
In cases where a transducer is required having high vibrating
amplitudes at the forward face and broadband (low Q) resonance
characteristics, then the choice of backslug material is important.
In such cases, the backslug material should have a high acoustic
impedance as compared to the forward slug. As is well known in the
art, this material impedance depends on a large degree on its
density and velocity of propagation. End face 11 and the outer
surface of rear slug 10 require no special finish other than rust
protection. The same is true of the surfaces of bore 14 and
counter-bore 15. Shoulder 16 however should be finished to a smooth
flat surface perpendicular to the slug axis and accurate to about
one thousandth of an inch.
Slug end face 12 which abuts a ceramic face must be carefully
prepared. The faces of ceramics should be flat to within one or two
ten thousandths of an inch and must be truly normal to the axis of
the ceramic discs. End face 12 of slug 10 must also be
perpendicular to the axis of slug 10 and must also be true to the
same degree as the ceramic face. The surface of face 12 is
preferably lapped but need not be highly polished. A satin or
etched surface will suffice. In preparing face 12, the fact that
face 12 will be tightly pressed against a ceramic face must be kept
in mind. Good results have been obtained in finishing surface 12 on
a precision surface grinder using an accurately dressed, fine stone
wheel. The ceramic material can resist compressive forces of great
magnitude. However, such ceramic materials are brittle and will
crack unless the matching surfaces are accurate. Some "coining" of
the silver coating on ceramics fills in microscopic irregularities
under the compressive forces used.
Referring now to the ceramics, two discs 20 and 21 have disposed
between then high potential metal disc electrode 22. As is well
known, ceramics 20 and 21 are poled so that the appropriate faces
are in the right direction. The polarities of the two ceramics are
such that when a high electric potential is applied across the
faces of each ceramic (the ceramic faces are electrically connected
in parallel) the reaction of the ceramics are mechanically aiding
so that essentially the two ceramics are in series mechanical
relation. This arrangement is well known in the art.
High potential electrode 22 consists of a metal disc having a
thickness of the order of about 3/16 of an inch. Electrode 22 may
be of any desired electrically conducting material such as
aluminum, brass, steel, etc., and has its opposite faces finished
to the same degree of accuracy as end face 12 of rear metal slug
10. Electrode disc 22 is thick enough to provide support for
electrical terminal 22a to which an insulated electrical conductor
may be connected. The ceramic assembly, including ceramics 20 and
21 and intervening electrode 22 have the same outer and inner
diameters. The inner diameter of the parts making up the ceramic
assembly is preferably somewhat larger than the diameter of bore 14
of rear slug 10 to accommodate tubular insulator 25, disposed
between the inner surfaces of the ceramics and electrode on the one
hand and outer surface of bolt 27 passing through rear slug 10 and
within insulator 25. Insulator 25 is made of material which is a
good electrical insulator and can withstand a reasonable degree of
heat and ultrasonic vibration. As an example, insulator tube 25 may
be of teflon or silicone rubber or fiberglass. Each of these
insulating materials can withstand temperatures of the order of
about 500.degree. F. Buna N and Neoprene rubber may also be used in
lower power units.
Ceramics now available can withstand temperatures of about
400.degree. - 500.degree. F. without undue depolarization. The
potentials used on ceramics are normally of the order of four or
five hundred volts for this type of structure. As a rule the
dielectric constant of the insulator is not important since the
operating frequencies, usually about 20KHz, are too low to result
in dielectric losses of any magnitude.
Bolt 27 is threaded along as much of the bolt length as necessary
to insure a firm grip with the internally threaded part of, in this
instance, a front horn.
Bolt 27 must have an overall length such that the bolt head at one
end and threaded portion at the other end are well spaced from the
ceramic assembly and the nodal plane region beyond ceramic 21, to
be described later. When a transducer assembly is ready for
operation, bolt 27 has a static tension which is uniform along the
bolt length. In transducer operation, dynamic conditions in the
transducer result in superimposing on bolt 27 added tensile forces
which may increase or decrease the normal bolt static tension. (It
is understood that bolt 27 should not have its tension reduced to
zero at any time.) When bolt 27 is subject to dynamic loading, it
is stressed to maximum values along its length and near the
transducer nodal plane and should have maximum metal to resist
tension. Hence it is desirable to have the threaded bolt part well
spaced as pointed out. The threaded bolt part however must be long
enough so that a strong coupling through the bolt threads can be
provided. As an example for the dimensions of ceramics given, the
threading should be about one-half or three-fourths inches
long.
Bolt 27 fits loosely within smooth bore 14 of rear slug 10 and the
bolt has head 29 dimensioned to fit within bore 15 of slug 10. Bolt
head 29 is generally of the internally wrenching type as the
so-called Allen type having a recessed hex so that a hexagonal rod
may be used to torque up the bolt. As is usual in this art, bolt 27
may be of high strength steel, or other fatigue resistant
materials, which can withstand a high tensile force used for
compressing crystals 20 and 21.
As previously set forth, bolt 27 is maintained in tension to a
predetermined value, about which value dynamic conditions incident
to acoustic transducer operation result in transient increase or
decrease of static bolt tension. It is desirable that the static
tension operating point be maintained at a constant value over
variations in temperature which might result in variations of bolt
length. Conical spring washers (Belleville) are provided for this
purpose and for convenience, one or more such washers are disposed
between the bolthead and shoulder 16 created by counterbore 15 at
the inner end thereof. If more than one such conical spring washer
is used, they may be arranged in any desired fashion (large end
opposed; small ends opposed) depending upon washer characteristics.
Such use of conical spring washer or washers maintains a
substantially constant bolt tension for static conditions in spite
of ambient temperature conditions.
Referring to tubular insulation 25, it is desirable that this fit
as snugly as possible to the inner surfaces of ceramics 20 and 21
and electrode 22. Insofar as bolt 27 is concerned, it is selected
to be of a length and having elastic properties consistent with
engineering requirements involved in tensioning the bolt to obtain
the desired amount of compression upon the ceramic assembly. It is
also desirable to have the diameter of bolt 27 as small as possible
and the diameter of head 29 as small as possible. While the tension
in bolt 27 serves to compress ceramics 20 and 21 on opposite sides
of high potential electrode 22, bolt 27 essentially is a foreign
but very necessary element. Care must be taken to avoid excessive
bolt length so that the resonant frequency of the bolt is not too
close to the resonant frequency of the transducer assembly. This
will minimize the interference between the acoustic energy of the
transducer proper and acoustic energy within bolt 27.
Bolted tightly to the threaded end portion of bolt 27 is forward
horn 30 of suitable metal such as hard aluminum, titanium alloy or
any other material having desirable acoustic transmission
properties as well as having sufficient toughness to withstand wear
and tear. As shown here, horn 30 has a tapered exterior surface
with rear face 31 and forward end face 32. Horn 30 has blind axial
recess 34 conveniently threaded at the forward part of the recess.
End face 31 of the horn presses against the outer face of ceramic
21 and accordingly requires a finished face which is true and
accurate to the same degree as face 12 of rear slug 10. Bolt 27 has
an unthreaded part of its length extending forwardly of rear horn
face 31 in a counter-bored rear portion of horn recess 34. The
threaded end portion of bolt 27 engages the blind threaded end
portion of horn 30 to permit horn 30 to be tightened on bolt 27
enough to tension bolt 27 to a prescribed value for compressing the
ceramics.
In assembling the transducer, it is preferred to dispose the rear
slug, ceramics, including the high potential electrode, and horn in
jigs to keep them in desired relative position while restraining
them against relative rotation to minimize torsional effects in
ceramics. The bolt and conical washer (or washers) are then
disposed in proper position and the bolt head is then turned to
create the desired bolt tension.
Front member 30 as illustrated in FIG. 1, is a horn whose small
forward end may function as a tool or may actually carry a tool for
applying acoustic energy to a load. Such a horn construction,
insofar as its forward end is concerned, is conventional.
Instead of horn 30, a cylindrical slug 30' shown in dotted outline,
may be used. Slug 30' will require the addition of suitable tool
members. Slug 30' will usually be shorter than horn 30. No attempt
has been made to show parts to scale. In all instances, the rear
part of the front member (horn or slug) will always have a
cylindrical portion 31. If slug 30' is used, it may be desirable to
have a bore through the entire slug length or have a threaded
recess at the forward end of the slug, generally similar to FIG. 5
extending forwardly of rear face 31 and carrying flange 38 integral
with member 30 or 30'. The overall length of the rear slug and
ceramic assembly on the one hand and length of front member 30 (or
30') on the other hand are such that the nodal plane is located at
flange 38, preferably the mid plane of flange 38, perpendicular to
the transducer axis. This means that front member 30 (or 30') will
have an overall length greater than one fourth of a wave length,
since that portion of the front member between rear end face 31 and
half of the flange thickness will constitute part of the rear one
fourth wave length of the transducer system.
Flange 38 preferably has a rectangular cross section providing side
walls 39 and 40 and peripheral outer wall 41. Flange 38 has a
thickness along the length of member 30 which is small in terms of
operating wave length but thick enough to be strong. Side walls 39
and 40 have curved fillets 39a and 40a where the metal runs into
the body of member 30. As an example, the transducer so far
described may have flange 38 about 1/32 of an inch in thickness.
The width radially of flange 38 may be any desired value and
theoretically this flange could extend outwardly for an indefinite
distance. This is because the nodal plane is located between side
walls 39 and 40 of this flange and thus the metal at or near the
nodal plane has substantially no longitudinal movement. For short
distances away from the nodal plane the amount of longitudinal
movement may be considered to be negligible. Consistent with
mechanical support requirements, the thickness of flange 38 should
be a minimum.
The entire transducer assembly is supported on opposite sides of
flange 38 by rings 45 and 46 of strong, rigid material, such as
aluminum. For the most part, rings 45 and 46 are alike, each having
body portion 50 and inner gripping or clamping portion 51. For
convenience, body portion 50 is ring shaped with outer circular
edge 52. The thickness of each ring may vary and as an example, for
the transducer described, the thickness of each ring may be about
five thirty seconds of an inch. The radial dimension of each ring
(the difference between the inner and outer ring edges) may also
vary widely and will depend upon mechanical considerations. As an
example, the distance between the inner and outer ring edges may be
about one-half inch. Each ring has outer face 53 and inner face 54,
the two rings normally being clamped tightly with inner faces 54
being in contact with each other.
To maintain rings 45 and 46 in tightly abutting face-to-face
relation, one of the rings, as 45 for example, has its body portion
50 provided with counter-sunk holes 56 and the other ring has
threaded holes 57, which register with counter-sunk holes 56 to
accommodate screws 58. As illustrated herein four such registering
sets of holes equally spaced around body 50 of each of the two
rings is provided. The remainder of body 50 of each of the rings
has closely spaced registering holes 59 to permit air to pass
through from one side of the two rings to the other side thereof.
As will be explained later, the entire transducer may be mounted
within a housing and rings 45 and 46, in the absence of holes 59,
would impede movement of air along the length of the transducer
assembly.
The diameters of holes 59 and the spacing between adjacent holes
are not critical. Instead of holes through the body of the two
rings, the outer edges of the two rings as assembled may be
scalloped to promote the passage of air through or past the rings.
The two rings are preferably made of aluminum, although brass,
steel or other material as non-metal may be used.
The construction of clamping inner portion 51 of each ring will now
be described. Rings 45 and 46 may have identical inner clamping
portions. The inside surface of clamping portion 51 of each ring
has a series of flat steps. Beginning with inner face 54 of each
ring, first step 61 has the maximum diameter and is large enough to
clear by a small fraction of an inch outer surface 41 of flange 38.
The axial dimension of each step 61 is more than one half the
thickness between flange side walls 39 and 40 as suggested in FIG.
4, sufficiently so that ring metal and flange metal will never
touch. When two rings are clamped together tightly, both steps 61
cooperate to encircle outer wall 41 of flange 38 having an annular
clearance such as about fifteen thousandths of an inch for the
example given. Next step 62 is dimensioned to engage the outer
surface of O-ring gasket 63 having a rectangular cross section.
Each clamping ring 45 and 46 cooperates with each of the two
O-rings 63. Ring 63 is of compressible or deformable material which
can withstand substantial heat and will not break down from
acoustic energy. As an example, such materials as silicone rubber,
Teflon, Buna-N and neoprene rubbers may be used. The normal cross
section of gaskets 63 is preferably rectangular and dimensions are
such that when the parts are assembled, adequate compression
results with substantially full contact between gasket surfaces and
metal established. It is possible to use O-rings of circular
section and correspondingly shape the surfaces engaging the
gasket.
It is important that relative rotary movement between the
transducer proper and its mounting be prevented. Such movement
might be at the surfaces of metal and material of gaskets 63.
Rotary movement there could result in broken wire leads. To avoid
such movement, it is possible to interlock the gasket material and
metal pressed against such gasket material. Thus side walls 39 and
40 of flange 38 could have indentations in the metal surface or
fine passages through the flange from one side wall to the other
side wall of the flange. Sharp edges in the metal should be
avoided. Similarly, the metal of ring parts 45 and 46 (or the
corresponding parts of the ring modifications) can be similarly
treated so that the gasket, under compression, will be locked
against rotary movement when the transducer is assembled. The
O-ring gaskets may be positioned on each flange side at an
appropriate time, when assembling, and cemented if desired.
The compression of the gasket material should be limited to avoid
increasing conductivity of gasket material to acoustic energy to an
undesirably high level. So long as the gasket material is soft
enough to permit relative play of the transducer and the mounting,
the gaskets, particularly in view of their proximity to the nodal
plane, will essentially isolate the transducer from acoustic energy
leakage at the mounting and prevent destruction of the mounting
system.
Step 65 is at the outer face 53 of each ring and has the minimum
inside diameter for each mounting ring. Gaskets 63 are normally
quite soft (for example a Durometer value of about 50 may be used)
but compression is sufficient to make the suspension stiff enough
to be workable. In any event, clearances and suspension stiffness
are such that any acoustic coupling from the transducer to the
mounting ring is via the gaskets only.
For a transducer operating at approximately 20 KHz, a 11/2 inch
diameter steel rear slug may have an overall length of about 15/8
inches, a forward aluminum 11/2 inch slug may have an overall
length of about 21/4 inches, two ceramics each about one-fourth
inch thick and a high potential electrode about 7/32 inches thick
may make up a trasducer having a half wave length of a bit over
41/2 inches. It is understood of course that the dimensions may
vary with design parameters. The nodal plane will be predetermined
to be at the flange mid section near the rear of the forward
member.
Instead of having a forward horn130 carry a tool at end 132, as
shown in FIG. 5, it is possible to add a resonant extension of
proper material, proper length and suitable acoustic impedance
characteristics.
The front member 30 (or 30') illustrated in FIG. 1, has flange 38
spaced away from end face 31 by substantially the thickness of a
gasket. This enables both gaskets to be positioned accurately on
opposite sides of flange 38 on the same member prior to assembling
clamping rings 45 and 46.
It is possible, however, to have flange 38 at the rear end of the
forward member so that a flange side wall is part of end face 31.
This is illustrated in FIGS. 5 and 6 which show a front member 130.
In this front member, the rear end portion of member 130 will be
cylindrical, even though the remainder thereof may have any desired
shape. One gasket ring will overlie the cylindrical portion of
member 130 forwardly of flange 38 while the companion gasket ring
will be disposed about the forward cylindrical end of the ceramic
part 21 of the system. When the outer clamping rings are applied to
each of the two gaskets in the form just described, it is possible
that one gasket may tend to be eccentric with respect to the other
gasket so that somewhat greater care in assembling the entire
structure may be required.
A housing for a transducer assembly will generally be a practical
necessity over the rear portion of the transducer beginning with
the mounting rings and extending rearwardly over the ceramics, high
potential electrode and rear slug. A simple housing 70 of generally
cylindrical construction may be provided. Housing 70 may either be
of synthetic material as plastic or may be of metal such as
aluminum of sufficiently heavy gauge to withstand rough use. While
a housing may be cylindrical, there is no particular necessity for
such a shape and, instead, the housing may have a rectangular cross
section. This, of course, would require a different shape for the
outer edges of the mounting rings or might require some adapter
between the inside surface of the housing and the outer portion of
the mounting rings.
A simple mounting for a transducer within housing 70 may have an
inwardly extending shoulder 71. The inside diameter of housing 70
may be large enough to accommodate the outer edge of the mounting
rings while inner shoulder 71 would provide a support against which
the mounting rings may be disposed and to which they could be
attached. As an example, inner shoulders 71 may be of aluminum and
have a series of holes registering with the holes in the mounting
rings. Retaining bolts may be used at a number of such holes to
attach the mounting rings to the housing shoulder. Any other
attaching means between housing 70 and the mounting rings of a
transducer may be used.
It may be desirable to provide a blast of cooling air for
dissipating any heat generated by the transducer unit. The
direction of flow of such a glast of air is preferably rearwardly
of the transducer beginning about at the mounting rings and
extending within the housing past the rear free end of the
transducer. By having the blast of air travel in that direction,
there will be less likelihood of air blasts on the work with
consequent blowing of fine particles. The air blast itself may be
provided in a number of ways as for example by fan 74 driven by
electric motor 75 supported within the housing. It is understood,
of course, that the rear end of the housing will be open to the
atmosphere so that a continuous blast of air may travel through the
holes in the mounting rings and over the exposed surfaces of the
ceramics, high potential electrode and rear slug.
Suitable wire leads for the electric motor, the grounded rear slug,
forward member or whatever metal parts are used forwardly, mounting
rings and housing, if of metal, are disposed within the housing. A
lead from the high potential electrode and a ground wire from the
mounting ring (if such mounting rings are electrically insulated
from the housing interior as would be the case in a housing of
plastic material) must be carefully located on the transducer as
close to the nodal plane as possible. Precautions conventional in
this art to prevent crystalization of wire are followed.
The mounting of a transducer may, in some instances, require some
differences in the mechanical construction of the mounting rings.
For example, rings 45 and 46 are circularly continuous. However, it
is possible to have a mounting ring assembly where a ring is
divided into two semi-circular portions each of which essentially
integrates half ring 146a and half ring 146b to extend over the
edge of flange 38. The two semicircular ring portions may be bolted
together by overlapping extensions as illustrated in FIG. 8. In
certain instances it may be desirable to have one of the mounting
rings - the one nearest to the outer surface of the ceramic --
circularly continuous and have a cooperating ring divided into two
semicircular parts. Such an arrangement is required for a horn
shown in FIG. 7, where the metal forwardly of flange 38 is
outwardly expanding so that a continuous ring cannot be used. In
such instances, a onepiece ring may be used on one side of the
flange and a composite split ring may be positioned on the other
side of the flange. The gaskets have sufficient elasticity to be
stretched over a flange.
Referring specifically to FIG. 8, one mounting ring, in this case
45, is circumferentially continuous and is provided with suitable
holes through the ring. This solid ring has a stepped interior
generally similar to the stepped interior of one of the two rings
illustrated in FIGS. 3 and 4. Solid ring 45 is adapted to go about
the cylindrical end of a horn such as, for example, shown in FIG. 7
on the side of the flange nearest the small end face of the
horn.
Split ring 146 has portions 146a and 146b which provide generally
semi-circular rear portions. At the split, the ring ends are
stepped as shown so that two semi-circular rings may be fitted to
make a complete ring. It is clear that the split ring may be
disposed about the narrow annular cylindrical surface of the horn
adjacent the flange but located on the far side of said flange away
from rear end of the horn. Be screwing or bolting the various parts
or the ring portions together, the entire mounting assembly for a
horn, such as illustrated in FIG. 7, may be provided to accommodate
an outwardly flaring horn surface.
Other ring splitting procedures may be adopted to permit mounting
of a transducer assembly for work.
It will be clear that the invention provides a transducer assembly
whose lateral mounting space requirements are minimized. Thus, a
transducer assembly of the type illustrated in the drawing (with or
without the housing as desired) may be disposed in close proximity
to similar transducers. The only clearance between adjacent
transducers is normally determined by the radial extension of the
flange beyond the outer surfaces of the transducer. Such economy of
mounting space permits of close disposition and operation of a
plurality of transducers. No attempt is made to show relative
proportions of radial dimensions of a transducer mounting flange
and the transducer proper. It is obvious that a number of
transducers can be mounted side by side on a plate and so closely
spaced that the outer flange diameters nearly touch.
It is possible to remove flange portions between adjacent
transducers to permit closer transducer spacing of a cluster of
transducers. Thus, instead of a 360.degree. continuous flange
mounting, cutouts of metal and gasket portions over small arcuate
regions about a transducer permit minimum spacing between
transducers for maximum application of acoustic energy at a given
locale.
* * * * *