|Publication number||US3727719 A|
|Publication date||Apr 17, 1973|
|Filing date||Jun 19, 1969|
|Priority date||Jun 19, 1969|
|Also published as||CA929109A, CA929109A1, DE2029073A1|
|Publication number||US 3727719 A, US 3727719A, US-A-3727719, US3727719 A, US3727719A|
|Original Assignee||Yando S|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (5), Referenced by (29), Classifications (7)|
|External Links: USPTO, USPTO Assignment, Espacenet|
[ 1 Apr. 17, 1973 United States Patent [191 Yando 3,240,289 3/1966 Kishi 3,275,100 9/1966 Dunning.................
154] SOUND REPRODUCING SYSTEM  Inventor:
Stephen Yando, Huntington, NY. 11743 Primary Examiner-Stephen J. Tomsk Attorney-Stefan J. Klauber  Filed: June 19, 1969  Appl. No.: 840,117
 ABSTRACT A dynamical system for the re production of sound. The system includes a relatively small enclosure with a driven loudspeaker cone and one or more free pistons ..............181/31 13 ...Gl0k 13/00, H04r 1/28 Field of Search......................................l8l/31.l
[521 511 int.
in the enclorigid shell having an opening juxtapositioned suspended in airtight fashion in openings sure. A to the driven cone, may surround the enclosur purposes of increasing the con  References Cited e, for pling among free UNITED STATES PATENTS pistons and between free pistons and the driven cone.
10 Claims, 7 Drawing Figures PEAK DISPLACEMENT of FREE PISTON PATENTEU APR 1 H973 8 (degrees) SHEET 1 OF 3 equilibrium plane u 24 WWW |4 IIHIHIIIIIIIII i3 Fig. l i
l 10/ l A? 1 M6 No he DAMPING E if V I2 I 3 v L x 4 i o v I i/ x= positive I xdirection MODERATE DAMPING LARGE DAMPING 0 f0 o Frequency Fly. 2.
NO DAMPING MODERATE DAMPING LARGE DAMPING Fig. 3.
IO- 1 I 0 f0 2% A Frequency lNVENTO/P.
STEEHEN YANDO PATENTEUAPR 1 7197s 3,727 719 SHEET 2 OF 3 lNVE/VTOR STEPHEN YANDO PATENTEDAPR 1 H915 3.727. 719.
SHEET 3 [IF 3 I equilibrium plane uswe 1 INVENTOH.
STEPHEN YANDO SOUND REPRODUCING SYSTEM This invention relates generally to loudspeaker enclosures but more specifically to a dynamic means for extending the frequency range and increasing the power output of a loudspeaker.
A loudspeaker is a device which converts electrical I energy into acoustical energy via its electromagnetically driven cone. The front and back surfaces of the moving cone radiate sound waves and these constitute the acoustical output of the loudspeaker device. it is the destructive interference between these two waves, especially at low frequencies, which has always constituted the major problem in sound reproduction. Loudspeaker enclosures represent attempts to control these interference effects for the purpose of extending the lower frequency limit of a loudspeaker.
The earliest loudspeaker enclosure" was based on the infinite baffle concept. According to this concept, the loudspeaker is mounted against a hole in a partition which extends to infinity in all directions. This confinesthe front and backside radiations to their respective hemispheres thereby eliminating all destructive interference effects. Even though the infinite baffle may be approximated by room partitions in practical situations, this approach was never very important because of its obvious costliness and inflexibility.
By folding a flat baffle into the form of an open backed cabinet a more practical form of speaker enclosure was evolved. The open backed cabinet is the most widelyused loudspeaker enclosure today. It is the lowest cost enclosure, especially when the loudspeaker shares the cabinet space with electronic components as in a TV or radio set. The performance of the open backed enclosure is rathermediocre however, and where cost is not the primary consideration more elaborate enclosures are used to obtain improved sound quality.
A popular speaker enclosure in this category is the bass reflex type which is a closed cabinet with a proportioned port or vent located near the loudspeaker diaphragm. Due to its cabinet-vent resonance, the bass reflex enclosure shifts the phase of the rearward speaker radiation as it emerges through the port to reinforce the forward speaker radiation. In good bass reflex designs, the low frequency cutoff may be extended almost one octave below that of an open backed enclosure of the same volume. The main factors which limit the usefulness of the bass reflex enclosure are its relatively large size and its moderately high cost in relation to its performance level.
With the recent trend toward cheaper and higher power audio amplifiers, the relatively inefficient but high performance acoustic suspension speaker enclosure has come into its own. This enclosure is a'fully sealed, rigid cabinet packed with sound absorbing material, which contains and dissipates the backside radiation of the speaker. Such speaker enclosures are relatively compact and are capable of fine performance as is attested to by their wide usage. On the debit side, it can be said that they are rather inefficient and fairly expensive to construct. Furthermore, a special problem exists because the confined air places an elastic constraint on the backside of the speaker cone, thereby raising its natural resonant frequency. The result is that the acoustic suspension cabinet, though smaller than the bass reflex cabinet, nevertheless has its own minimum volume requirement for any given level of performance.
Other speaker enclosures do exist which provide excellent performance but are not very widely used because they are larger and costlier than acoustic suspension systems. When viewed with respect to this present state-of-the art, the present represents an advance which will improve sound reproduction systems in the following ways;
It is an object of this invention to provide a sound reproduction system which is less costly than present types.
Another object of this invention is to provide a sound reproduction system which is more compact than present types.
Yet another object is to provide a sound reproduc tion system which will provide a higher level of performance than is possible in present types.
Still another object of this invention is to provide a more efficient sound reproduction system which derives useful acoustical radiation from the motion of the back surfaceof the speaker cone.
And finally, a further object of this invention is to provide a sound reproduction system which acts as an improved acoustic transformer and thereby increases the bass frequency power output of the loudspeaker.
The present invention is not to benarrowly classified as a loudspeaker enclosure because in reality it is a dynamical system of masses and elastances activated by an electrodynamic loudspeaker. By controlling the vibrational energies of the masses and elastances, the dynamical system creates acoustic radiations which augment those of the loudspeaker over a predetermined low frequency range. More specifically, the present invention consists of an airtight chamber with an electrodynamic loudspeaker mounted on one of its sides. At least one of the other sides of the chamber is flexibly suspended so it can move inwardly and outwardly with respect to the enclosed volume. The mass of the suspended side which we shall refer to as a free piston, is chosen to resonate with the effective elastic stiffness of the dynamical system at a'predetermined frequency within the low frequency range.
When the voice coil of the loudspeaker is energized, its moving cone radiates acoustic energy directly from its front surface while its back surface, acting as a piston, modulates the air pressure within the chamber. These pressure modulations cause the free piston to vibrate characteristically; the greatest vibration occuring at a frequency where the mass of the free piston resonates with the effective elastic stiffness of the dynamical system.
At frequencies approximately equal to and greater than this frequency the acoustic radiation from the free piston will reinforce the direct loudspeaker radiation, resulting in an increased acoustic output. By a suitable choice of dynamical system parameters of which the system resonant frequency is but one, the acoustic output of the loudspeaker may be significantly enhanced over the low frequency range.
After the foregoing introduction it becomes appropriate to examine the present invention and its objects in more complete detail. This objective will be acinvention FIG. 1 is a cross-sectional perspective view taken at the central plane of symmetry which depicts the basic embodiment of my invention.
FIG. 2 is a diagram which shows the free piston vibrational amplitude characteristic as a function of frequency.
'FIG. 3 is a diagram which shows the free piston vibrational phase characteristic as a function of frequency.
FIG. 4 shows an electrical circuit whose electrical behavior is analogous to the acoustical behavior of the embodiment of FIG. 1.
FIG. 5 is a cross-sectional view taken at the central plane of symmetry of a second embodiment of my invention.
FIG. 6 is a cross-sectional view taken at the central plane of symmetry of a third embodiment of my invention.
FIG. 7 is a cross-sectional view taken at the central plane of symmetry of a fourth embodiment of my invention.
Referring to FIG. 1 there is shown a rigid walled airtight chamber 10, typically of wood construction, having two openings 1 l and 12 in its front face. Although a wood chamber is suggested, any other construction material such as plastic or metal would be equally satisfactory. A rigid plate 13, hereinafter to be referred to as the free piston 13 is suspended in opening 11 on an elastic membrane 14. Said membrane 14 permits the free piston 13 to move to and fro about the equilibrium plane and also acts as sealto prevent the passage ofair into and out of the chamber through opening 11. The mass of the free piston 13, is so proportioned as to cause said free piston to resonate with the effective elastic stiffness of the dynamical system at a specified frequency within a predetermined low frequency range. Two sources; the enclosed air volume 24, and the elastic membrane 14 contribute to the elastic stiffness of the dynamical system. Normally, a minimum system stiffness is. desired and under such. circumstances the use of 'a' supple elastic membrane is indicated. A supple piston suspension, however, is not mandatory since stiff piston suspensions for the adjustment of the free piston resonant frequency are also envisioned within the scope of the invention.
A loudspeaker generally designated by the numeral 15, and most typically of the electrodynamic typeis mounted against and seals opening 12 of the airtight chamber 10. The loudspeaker cone is represented diagrammatically by the rigid plate 16 with its elastic suspension 17. The rigid plate 16 will hereinafter be referred to as the actual piston 16. Two input terminals 18 and. 19 passing through the walls of the chamber 10 in a substantially airtight manner are connected to voice coil terminals 20 and 21 with conductors 22 and 23. Circular shapes were chosen for the openings ll, 12, and the free piston 13, and the actuated piston 16 and all the other embodiments are assumed to have circular pistons as well. These choices are based on convenience rather than necessity and are not to be construed as a limitation on the geometry of the actuated or free pistons because other geometrical shapes would serve equally well.
In operation, an electrical current is applied to terminals l8 and 19 and this will produce a displacement x. of the actuated piston 16 from its equilibrium plane.
This displacement will produce a pressure change within the airtight chamber which in turn will cause the free piston 13, to be displaced a distance x from its equilibrium plane. These displacements result in a change of the enclosed volume 24. At any given instant in time the volume of the chamber 10 may be expressed as,
v V+ (Jt A, X4) where v the instantaneous volume of the chamber V= the equilibrium volume of the chamber when P=( (2) where p the instantaneous pressure within the chamber E P chamber pressure at equilibrium volume atmospheric pressure 14.7 psi.
The exponent n can be between unity for an isothermal processand l .4 for an isentropic process. In practice, n will be between these extremes and will be dependent upon the frequency of the pressure cycle and the rate at which the enclosed air can exchange heat with its surroundings.
The instantaneous pressure changes within the chamber result in a pressure differential applied over the cross section of the free piston 13. This'pressure differential produces a force on the free piston which under typical circumstances is very closely given by:
x =X Coswt. (5)
where W= 2'nf and f frequency of the displacement then solution of equation (4) reveals that the displacement x of the free piston will be;
where the phase angle, 0, is defined by the implicit relationship:
Equations (6) and (7) reveal that the amplitude and the phase of the free piston motion are frequency dependent. An examination of equation (6) shows that the displacement of the free piston will be a maximum at the frequency f,, where U 1 K m a.
The frequency f,,, shall hereinafter be referred to as the dynamical system resonant frequency. The special significance of this frequency becomes apparent upon examination of FIGS. 2 and 3.
FIG. 2 shows the relative magnitude of the displacement of the free piston in terms of the actuated piston displacement as a function of frequency. FIG. 2 shows that the motion of the free piston is profoundly influenced by the damping factor. By damping is meant the ratio of the energy lost from the dynamical system per cycle of vibration to the total energy stores in said dynamical system. The major fraction of this energy loss" is in fact represented by the useful sound energy which is radiated from the outer face of the free piston. In an ideal case where no damping exists the free piston displacement increases without limit at the resonant frequency f and then gradually becomes smaller and smaller as the frequency increases. This resonant peak reduces to a finite value for moderate degrees of damping and actually vanishes as shown for large damping factors.
FIG. 3 shows the phase angle 0, of the free piston displacement with respect to the actuated piston displacement. This figure reveals that 0 is equal to 180 at very I low frequencies. This means that an inward or negative free piston displacement will result from an outward or positive actuated piston displacement. That this should be so is obvious when we realize that an outward movement of the actuated piston creates a'low pressure in the chamber which in turn causes the free piston to be pushed inward by the external atmospheric pressure. As the frequency increases, the free piston mass causes its displacement to lag the chamber pressure excursions so that 0 decreases to 90 at f and approaches zero as the frequency increases beyond f,,. The acoustic radiations from the outer surfaces of the actuated and free pistons bear the same relative phase relationships as do their respective displacements. Thus, the acoustic radiation from the free piston will significantly reinforce that from the actuated piston at all frequencies higher than the dynamical system resonant frequency. In accomplishing this result, this dynamical system extends to the output of a loudspeaker to lower frequencies than has heretofore been possible with loudspeaker systems of comparable volume. FIG. 3 reveals another important characteristic of the present invention. Because the actuated and free piston displacements are substantially in phase above the dynamical system resonant frequency, large pressure variations are produced in the airtight chamber which oppose the motion of the actuated piston. This restraining action loads the actuator motor and enables the system input power to be increased without driving the actuated piston beyond its limits of linearity. This unusual power handling capability stems from the isobaric specification for the enclosed volume of the airtight chamber, a specification which tightly couples the free piston to the actuated piston over the entire low frequency range. As a result, this dynamical sound reproducing system can obtain considerably more undistorted low frequency power from a given loudspeaker than is possible in any existing loudspeaker system.
FIG. 4 shows an electrical circuit whose electrical behavior is analogous to the kinematical behavior of the dynamical system of FIG. 1. The circuit parameters of FIG. 4 are related to the parameters of the dynamical system by the relationships:
electrical energy dissipated in the resistance R represents the acoustic energy which is radiated from the free piston plus the small frictional losses in the dynamical system, and the electrical charge on the capacitor C represents the displacement, x, of the free piston. The inductance, L, is seen to be related to the proportions of the free piston and the enclosed volume of the dynamical system. Together the R, L, and C elements form a series circuit which resonates at f,,, the dynamical system resonant frequency.
Dynamical systems more complex than the embodiment of FIG. 1 are also envisioned within the scope of the present invention. For example, several free pistons proportioned to resonate at several frequencies could be employed in the dynamical system. Under such circumstances, a network more complex than the series circuit of FIG. 4 would be necessary to simulate the broader band behavior of the several free pistons.
FIG. 5 shows a second embodiment of my invention.
In this figure there is shown a substantially rigid airtight chamber having a large opening 111 in its front face. A rigid plate I13, hereinafter to be referred to as the free piston 113, is suspended in opening 111 on an elastic membrane 114. Said membrane 114 permits the free piston 113 to freely move to and fro about its equilibrium plane and also acts as a seal to prevent the passage of air into and out of the chamber 110. An opening 112 is provided in the free piston 113. A loudspeaker 115 most typically of the electro dynamic type is rigidly mounted against and seals the opening 112 of jection'able vibrations.
the free piston 113. The cone structure of this loud speaker is represented diagrammatically by the rigid plate 116 and the mounting membrane 117. The rigid plate 1 16 will hereinafter be referred to as the actuated piston 116.
Two terminals 118, and 119 passing through the chamber 110 wall in an airtight manner are connected- FIG. 5 are similar to that of FIG. 1 with an exception due to the mounting of loudspeaker 115 upon the free piston 113. Thus the frame and magnetic structure of the loudspeaker become an integral partof the free 7 piston while the speaker cone or actuated piston, 116, suspended within the loudspeaker frame, retains its capacity for an independent motion relative to the free piston 113. The actuated piston displacement, x,,, relative' to its own frame represents only a portion of its total displacement. The free piston displacement, x, is added to the relative displacement, x 'to give the actuated piston,-116, a total displacement of x x,,. This result serves to effectively increase the displacement capability of the loudspeaker thereby further improving its capability to produce bass frequencyacoustic powerIT-he embodiment of FIG. 5 will often times be preferred over that of FIG. 1 because it can provide improved performance at an equal or smaller cost. It may not always be possible however, to create a dynamical system based on the embodiment of FIG. 5 due to" sive, objectionable vibrationswill be induced inthe a The embodiment of FIG. 6 represents a very simple dynamical system which is a highly satisfactory sound reproducer. A somewhat more complex embodiment with an even more enhanced low frequency output is shown in FIG. 7. This embodiment achieves its improved capability by increasing the acoustical interaction .or coupling between the several'pistons of the dynamical system; As is evident in FIG. 7, this important result is accomplished by mounting the embodiment of FIG. 6 on standoffs, 327, within an outer shell generally designated by the numeral 328. The numerals 310 through 326 represent the same details which were identified with the numerals 210 through 226 respectively in FIG. 6. The outer shell, 328, typically of wood construction, consists of substantially rigid non-movable surfaces and is provided with a port, 329, in a position preferably juxtaposed with the actuated piston, 316. Although a wood outer shell is suggested, any other construction material such as plastic or metal would be equally satisfactory. Two input terminals 330 a and 331 are mounted in a substantially airtight manner that thedistance' from the most remote point, A, on
free piston 325,- taken along dotted line B to the port, 329, is smallfcompared to the acoustic wavelengths in the prescribed low frequency range. This being so, the
space, 334, between-the chamber, 310, and the 'outer shell, 328, can be regardedas a conduit for commubody of the airtight chamber and transmittedto the surnicating' the acoustic pressure modulations, created by free pistons,'313 and 325, to the actuated piston, 316,
and the port, 329: The establishment of this short conduit has the effect of increasing the mutual acoustical coupling between pistons 313, 316-, and 325 thereby causing an increased loading on theactuated piston, 316, and resulting in an increased power output over the prescribed low frequency range. In the :mid and high frequency ranges, free pistons, 313 and 325 are quiescent and so make no contribution to] the sound 1 output and none is needed however, since. the actuated referred toas free piston 225 is suspended within the 1 opening 224' with the elastic membrane 226. The
elastic membrane 226 permits the free piston 225 to move freely to and fro about its equilibrium plane and also acts as a seal to prevent the passage of air intoand lOUt of the airtight chamber 210. The mass andcro ss' sectional area of free piston 225-is adjusted to be substantially equal to that of free piston 213. This adjustw ment' assures that" freefpistons 213 and 225 will resonate with 'theelastic stiffness of the dynamical piston, 316,- can generate adequate amounts of acoustic power in these ranges.
The foregoingv specifications" have described "a dynamical system for extending the lowffrequen'cy' range of a loudspeaker and forincreasing its power out-- the presentinvention is based. Accordingly, the specifisystem at one and the-same predetermined frequency.
Under this circumstance, "themo menta of free pistons 213 and 225v will be'equal but oppositely directed thereby. creating a dynamic balance which will leave cations shall be interpreted merely asfillustrativje' and not limitingin any sense.
What is claimed as new is: i j
l. A dynamical system for the reproduction of sound which consists relatively small :substantially airtight.-
chamberhaving a plurality of .openings, withrigid platescompliantly suspended in' an airtight manner inmanner within an opening in one of said plates, the
cone of said electrodynamic speaker being vibrated by the passage of electrical current through the voice coil of said electrodynamic loudspeaker, the mass and area of each of the said plates being proportioned so that at least one of said plates will be vibrating substantially in unison with the said speaker cone at each interval within a prescribed low frequency range, the plurality of the said plates being spatially arranged so as to minimize their combined momentum and a substantially rigid outer shell enclosing the airtight chamber for increasing the acoustical power output of the electrodynamic speaker, said outer shell provided with an opening juxtaposed to the loudspeaker cone.
2. A dynamical system for the reproduction of sound according to claim 1 and whose airtight chamber is proportioned so that its enclosed volume is substantially isobaric over said prescribed low frequency range.
3. A dynamical system for the reproduction of sound according to claim 2 where the mass and area of the plurality of the said plates are proportioned to vibrate at one and the same characteristic frequency, and substantially in unison with the'said loudspeaker cone over the said prescribed low frequency range.
4. A dynamical system for the reproduction of sound, comprising:
a relatively small substantially airtight enclosure having a first opening on one side thereof;
a free piston in the form of a first rigid plate suspended in airtight fashion in said first opening by compliant means sealing the space between said plate and first opening; and
actuated loudspeaker cone compliantly suspended in a second opening within said first rigid plate by compliant means sealing the space between said cone and said second opening. 5. A system in accordance with claim 4, further including at least an additional free piston compliantly suspended in airtight fashion in an opening formed in the wall of said enclosure, the spatial arrangement of the totality of said free pistons being such that the momenta of the several free pistons substantially cancel one another.
6. A system in accordance with claim 5, wherein said additional free piston comprises a second rigid plate mounted in a third opening at the wall of said enclosure opposite that bearing said cone and said first plate, said second plate being suspended in said third opening by compliant means sealing the space between said plate and said third opening.
7. A system in accordance with claim 5, further including a substantially rigid shell enclosing said dynamical system for increasing the acoustical coupling among free pistons and between free pistons and cone and thereby increase the power output of said system over its low frequency range, said shell being provided with a port juxtaposed to said driven cone for radiating sound energy from said system.
8. A dynamical system for the reproduction of sound, comprising:
a relatively small enclosure having at least one actuated loudspeaker cone and at least one free piston suspended in airtight fashion in openings in the walls thereof; and
a substantially rigid shell enclosing said small enclosure for increasing the coupling between said piston and cone an thereby increasing the power output of said dynamical system over the low frequency range of said system, said shell being provided with an opening in a position juxtaposed to said cone for radiating the sound energy output of said dynamical system.
9. A system in accordance with claim 8, including a plurality of said free pistons, the spatial arrangement of said pistons being such that the momenta of the several pistons substantially cancel one another.
10. A system in accordance with claim 9, wherein said free pistons comprise rigid plates.
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|U.S. Classification||381/349, 381/345, 181/155, 381/338|