Abstract:
A method and an apparatus or apparatus system for vibration control, by harmonic optimization technology, of vibrations in the cantilever or barrel, portion of a device from which a projectile is fired or launched along the centerline of the cantilever. More particularly this invention relates to rifles, where the rifle barrel is a cantilever portion, and methods and apparatus for increasing the accuracy of firing projectiles. The invention is principally directed to a method and apparatus including a mass device affixed to a flexible cylinder extension at the muzzle end, inertial mass devices, having combustion pressure reduction features, affixed intermediate the muzzle end and the cartridge chamber, and a spring suspension system between barrel and rifle stock affixed proximal to the cartridge chamber. This system decreases the angular dispersion of barrel vibrations at the muzzle resulting from the firing of projectiles through such barrels.

Description:
CONTINUATION IN PART APPLICATION 
     This is a Continuation In Part Application from the nonprovisional parent application 08/846,375 entitled HARMONIC OPTIMIZATION SYSTEM FOR RIFLES to Roblyer et.al. as filed Apr. 30, 1997, now U.S. Pat. No. 5,798,473 and from the Continuation In Part application Ser. No. 09/053,912 entitled HARMONIC OPTIMIZATION TECHNOLOGY FOR RIFLES to Roblyer et.al. as filed Apr. 2, 1998, now abandoned. The applicants request prosecution pursuant to 37 C.F.R. 1.53(b) and 1.78 and 35 U.S.C. 120. New matter added herein will be set out separately, for examination convenience, in a separate letter transmitted with this CIP application. 
    
    
     FIELD OF THE INVENTION 
     The present invention relates generally to apparatus with a cantilever portion from which a projectile is fired or launched along the centerline of the cantilever and in particular to the controlling of vibrations of the cantilever component of such an apparatus. More particularly this invention relates to rifles, where the rifle barrel is a cantilever portion, and methods and apparatus for increasing the accuracy of firing projectiles. The invention is principally directed to a method and apparatus including a mass device affixed to a flexible cylinder extension at the muzzle end, inertial mass devices affixed intermediate the muzzle end and the cartridge chamber, and a spring suspension system affixed proximal to the cartridge chamber. This system decreases the angular dispersion of barrel vibrations at the muzzle resulting from the firing of projectiles through such barrels. 
     BACKGROUND OF THE INVENTION 
     Accuracy and consistency in striking a target is a principal goal of marksmen in hobby and military applications. A non-military application involves rifle target shooting competitions. Methods and apparatus have been developed with the intent of reducing factors which adversely affect accuracy and consistency in the delivery of a projectile at a target. Several solutions have addressed the issue by modifying the barrel or cantilever portion of the device of concern. The focus of such changes have involved the positioning of a mass or muzzle brakes at the muzzle end of a rifle barrel and the use of bench rests during firing. Prior art notes two of the factors adversely affecting accurate rifle marksmanship to be barrel vibration and recoil with solutions posed in the form of modification of the barrel or cantilever portion of the projectile firing or launching mechanism and in the development or change of firearm supports. U.S. Pat. No. 5,279,200 of Jan. 18, 1994, reissued as U.S. Pat. No. RE 35,381 of Nov. 26, 1996 to Rose et. al. recites the state of the art relating to reduction of vibration in rifle barrels observing that with such advancements target pattern inconsistencies remained as an inherent characteristic of rifles. Such a characteristic applies, by extension, to the apparatus which incorporates a cantilever for final projectile travel and exiting in determining the projectile trajectory. The &#39;200(RE 35,381) patent notes, for the rifle marksman, that inconsistencies are of particular concern in the firing of certain factory loaded cartridges from a firearm not designed specifically for use with that particular factory cartridge. The issue of matching a particular rifle with a particular cartridge, as a recognized method of adjusting vibration frequency so that the vibrational velocity is nearly stopped when the bullet exits the muzzle and increasing consistency, is addressed in the &#39;200 patent. The patent to Rose, et. al, discloses the ability to match a rifle to a particular ammunition and that with appropriate system adjustments, of the position of a mass at the muzzle, to fire different factory loaded cartridges. 
     Rose, in the &#39;200 patent, recites U.S. Pat. No. 4,726,280 to Frye disclosing a muzzle member at the muzzle end of a gun barrel. Although not stated in U.S. Pat. No. 4,726,280, it is generally understood that such a muzzle member may serve as a mass for the purpose of vibration dampening. The muzzle member is threaded onto the barrel, and is locked in place. Anschutz and Co. G.M.B., through the 1989 catalog of its distributor, Precision Sales International, Inc., of Westfield, Mass., discloses, at pages 11 and 16, barrel extensions for rifles that include removable weights. Although not stated in the 1989 catalog of Anschutz and Co. G.M.B., it is understood that varying such masses will enable a marksman to vary the dampening effect in relation to the barrel vibrations resulting from the discharge of different cartridges. 
     Prior art also addresses muzzle brakes in functioning to exhaust propulsion gases as a means of reducing recoil and of dissipating propulsion gases in a direction or directions other than out the muzzle of the barrel. Attention is called to U.S. Pat. Nos. 5,279,200(RE 35,381) to Rose; U.S. Pat. No. 4,879,942 to Cave and U.S. Pat. No. 5,092,223 to Hudson. The known muzzle brakes comprise a mass and are recognized to change vibration characteristics potentially performing a dampening function. 
     Firearm rests and supports may also perform a dampening or control function. U.S. Pat. No. 5,058,302 to Minneman, U.S. Pat. No. 4,971,208 to Reinfried et. al, U.S. Pat. No. 5,173,563 to Gray and U.S. Pat. No. 4,558,532 to Wright are noted. The foregoing patents and printed publications are provided herewith in an Information Disclosure Statement in accordance with 37 CFR 1.97 with the exception of the reference to Anschutz and Co. G.M.B. which has been obtained and submitted. Additional domestic and foreign patents and publications have been submitted in the prosecution of the parent application. This Continuation in part relies on and incorporates prior art as submitted and identified in Information Disclosure Statements in accordance with 35 CFR 1.97 in association with the parent application Ser. No. 08/846,375. 
     SUMMARY OF THE INVENTION 
     The present invention discloses a vibration control system developed by use of harmonic optimization technology (H.O.T.). The H.O.T. system addresses the improvement of rifle accuracy by controlling barrel vibration in a manner differing from approaches of other methods such as using extra heavy (bull) barrels, “tuning” cartridges with powder loads and bullet weight, or varying barrel vibration frequency with an adjustable mass at the muzzle. 
     Variations in either powder loads or bullet weights cause changes in muzzle velocities which result in different times between powder ignition and the time when the bullet leaves the muzzle. The barrel undergoes many complex and superimposed vibrations when the powder is ignited and the bullet is progressing down the barrel. Vibration dampening or minimization methods known in the prior art are directed to tuning the time the bullet leaves the muzzle with the barrel vibrational frequency. The intent of such tuning is to result in the bullet exiting from the muzzle at a time corresponding to a major vibrational mode at its position of extreme deflection. 
     A particular load will have some muzzle velocity variation from cartridge to cartridge, so that any variation in the angular deflection of the muzzle in time will result in a statistical variation in dispersion angle. Minimizing the time rate of change of the muzzle deflection, coupled to statistical variation in muzzle velocity, and thus the time of flight of the bullet to the exit point at the muzzle, will minimize group size making the rifle less sensitive to small variations in the bullet travel time. While this will reduce the group size of bullet impact, the point of impact may vary significantly with different loads and bullet weights inasmuch as the objective of the approach was to make the bullet exit the barrel while it was at the point of extreme deflection. This extreme deflection may direct the muzzle at different points of impact for different loads. 
     A system or apparatus for a rifle barrel, and other devices employing a cantilever portion from which a projectile is launched or fired, developed through a harmonic optimization technology achieves improved bullet accuracy by significantly reducing the magnitude of the barrel muzzle angular dispersion caused by vibrations. Thus, the specific sight-in for different loads will be more predictable, i.e., from exterior ballistics. Deviation of the point of impact from the ideal predictions of exterior ballistics will be minimized. Bullet accuracy will be less sensitive to variations in ammunition loads. 
     The vibrations affecting bullet accuracy are a superposition of many transverse vibrational modes that are initiated at a continuum of points along the barrel. The short-term vibrational response will include a particular solution arising from the specific characteristics of the driving function, but the vibrational response will rapidly transition into the natural vibrational modes for the barrel itself. Harmonic optimization technology recognizes that barrel vibration is unavoidable. This technology and invention focuses on control of barrel vibration in such a way as to minimize the dispersion angle at the muzzle, for all relevant time during the transit of a bullet, until the bullet leaves the barrel at the muzzle. The preferred embodiment of this invention addresses the short-term vibrational transient response of the barrel, in the vicinity of the muzzle, to the vibration caused by the combustion of a cartridge, in the cartridge chamber, and the transit of a bullet through the barrel. Another embodiment addresses the partial cycle of the lowest frequency mode and the higher-order vibrational harmonics of the barrel as presented in the parent application Ser. No. 08/846,775. This Continuation in part addresses the embodiment where the invention or system is optimized or tuned based on the short term vibrational transient response. 
     The present invention comprises an improvement to known vibration dampening systems or apparatus by first reducing vibrations at the muzzle by first partially decoupling and isolating the vibrations initiated in the barrel near the cartridge chamber or breach end of the barrel as a result of a launching and the transit of a projectile through the barrel, thereby reducing vibration transmission to the muzzle end of the barrel. The launching may be by, but need not be limited to, chemical, thermodynamic, or electromagnetic processes. Secondly, the vibrations are modified so that the angular dispersion at the muzzle, which gives final direction to the projectile, is minimized. This may be accomplished by a method which comprises tuning the barrel to produce a standing wave, corresponding to the frequency of the short term vibrational response, in response to barrel vibrations that bend the barrel proximal to the muzzle so that the dispersion angle at the muzzle remains nearly parallel with the bore axis. This method allows the projectile to exit the barrel at a point where the standing wave has maximum displacement or zero slope. In the preferred embodiment of the apparatus disclosed, the standing wave is produced by a harmonic oscillator and an inertial mass. However, it will be apparent to those skilled in the art that other hardware configurations will produce such a standing wave in response to the short term vibrational response of the barrel. The appended claims are therefore intended to cover all such configurations as fall within the true spirit and scope of the invention. Thirdly, the pressures of expanding gases on the back of the bullet as it exits the muzzle are reduced in order to prevent undue upset on the bullets&#39; angle of flight and axis of rotation. Moreover, in devices such as rifles comprising a barrel and a rifle stock, said method further comprises the step of adjusting the vibrational boundary conditions between the barrel and the rifle stock. Thus bullet path dispersion is minimized, not just for a particular load, but for any load with variations in bullet weight and powder load. The impact location of a specific bullet weight and powder load will be primarily a vertical relationship to the point of aim which is based on the predictable trajectory of the bullet. 
    
    
     BRIEF DESCRIPTION OF THE DRAWINGS 
     The foregoing and other features and advantages of the present invention will become more readily appreciated as the same become better understood by reference to the following detailed description of the preferred embodiment of the invention when taken in conjunction with the accompanying drawings, wherein: 
     FIG. 1 is a side elevation of a rifle showing the positioning of the components of the harmonic optimization system for rifles including the harmonic oscillator, shown as detail  14 , the inertial mass, shown as detail  8 ′, and the barrel spring suspension system, shown as detail  2 . The harmonic oscillator and inertial mass may be components affixed to the barrel or may be formed integral with the barrel. 
     FIG. 2 is a side elevation of the barrel spring suspension system. 
     FIG. 3 is an end elevation of the barrel spring suspension system using leaf spring suspension showing the housing with components of upper and lower housings. 
     FIG. 4 is a section showing the barrel spring suspension system using leaf spring suspension and a cross section detail of a leaf spring. 
     FIG. 5 demonstrates a leaf spring. 
     FIG. 6 is an end elevation of the barrel spring suspension system using coil spring suspension showing the housing with components of upper and lower housings. 
     FIG. 7 is detail  7  from FIG. 6 showing the use of coil spring as suspension. 
     FIG. 8 shows the inertial mass showing the perimeter, first and second ends, second annulus gas port and rifle barrel. 
     FIG. 8A is an isometric representation of the inertial mass showing the perimeter, first and second ends, second annulus gas ports, inertial mass bore, inertial mass axis and interior perimeter. 
     FIG. 9 shows the inertial mass showing the second end, second annulus gas ports, rifle barrel and barrel bore. 
     FIG. 9A is a first end elevation showing the first end, retaining bolts, barrel and barrel bore. 
     FIG. 10 demonstrates section  10  from FIG. 8 showing the inertial mass, perimeter, rifle barrel, discontinuity groove, discontinuity apertures, first and second annulus, first and second annulus gas ports. The method of retaining the inertial mass in place is shown by detail  13  in the use of a tapered split ring having a beveled surface, a ring gap and a spring function. The tapered split ring is bound by friction against the barrel by the force of a locking collar having a locking collar bore which bears against the beveled surface. The inertial mass bore bears against the beveled surface with retaining bolts securing the locking collar and inertial mass causing the tapered split ring to bind in place by friction. The inertial mass bore, proximal to the first end, and the locking collar will have a beveled surface to receive and bear against the tapered split ring. 
     FIG. 11 shows section  11  from FIG. 10 demonstrating the rifle barrel, discontinuity apertures from barrel bore to barrel surface and structural components of the inertial mass including discontinuity groove, first annulus, first annulus gas ports and inertial mass perimeter. 
     FIG. 12 shows section  12  from FIG. 10 demonstrating the rifle barrel, discontinuity apertures from barrel bore to barrel surface and structural components of the inertial mass including discontinuity groove, first annulus, first annulus gas ports and inertial mass perimeter. 
     FIG. 13 shows the tapered split ring as a means of securing the inertial mass in position. The beveled surface and ring gap are shown. 
     FIG. 14 shows the harmonic oscillator with harmonic oscillator mass, flexible cylinder extension, flexible cylinder extension wall, and flexible cylinder discontinuities with circular cross sections 
     FIG. 14A shows the harmonic oscillator with harmonic oscillator mass, flexible cylinder extension, flexible cylinder extension wall, and flexible cylinder discontinuities in the form of slits. 
     FIG. 14B shows the harmonic oscillator with harmonic oscillator mass, flexible cylinder extension, flexible cylinder extension wall, and flexible cylinder discontinuities in the form of grooves in the flexible cylinder extension wall. 
     FIG. 15 shows section  15  from FIG. 14 showing the harmonic oscillator with harmonic oscillator mass, flexible cylinder extension, flexible cylinder extension wall, flexible cylinder discontinuities, flexible cylinder bore, barrel with barrel bore and barrel axis and with the harmonic oscillator mass affixed to the flexible cylinder extension with threaded means. 
     FIG. 15A shows section  15  from FIG. 14 showing the harmonic oscillator with harmonic oscillator mass, flexible cylinder extension, flexible cylinder extension wall, flexible cylinder discontinuities, flexible cylinder bore, barrel with barrel bore and barrel axis and with the harmonic oscillator mass affixed to the flexible cylinder extension with welded means. 
     FIG. 16 shows an example of a computer simulation of the transient vibrational response (transverse displacement) at a time coincident with a bullet leaving the muzzle. This is a depiction of the expected response without use of the subject invention. 
     FIG. 17 shows an example of a computer simulation of the transient vibrational response or short term vibrational response (transverse displacement), with the harmonic optimization technology for rifles, at a time coincident with a bullet leaving the muzzle. The slope of this curve at the muzzle (the point where the bullet loses physical contact with the barrel) is thus controlled to remain more parallel to the baseline bore axis as compared to FIG. 16, demonstrating a reduced angular dispersion. 
     FIG. 18 shows a comparison of the computer simulations resulting in predictions of the slope of the barrel at the muzzle plotted against a time interval that includes the exit time of the bullet at the muzzle. This slope is proportional to dispersion angle. With the addition of the current invention, this dispersion angle is reduced significantly for all relevant time. 
    
    
     DETAILED DESCRIPTION 
     The harmonic optimization technology vibration controlling system  1  disclosed herein is illustrated in FIG.  1  through FIG. 15 as applied to a rifle  5  having a barrel  7 , a barrel bore  8 , a muzzle  9 , a cartridge chamber  11 , a bore axis  13 , a barrel surface  14  and a bore surface  8 A. The cartridge chamber  11  is distal from the muzzle  9 . The barrel  7  having a short term vibrational response, to the combustion of a cartridge in the cartridge chamber  11  and to the transit of a bullet through the barrel  7 . The muzzle  9  having a dispersion angle relative to the bore axis  13 . System components, in the preferred embodiment, include a harmonic oscillator  15 , formed at or affixed by means at the barrel muzzle  9 , the harmonic oscillator  15  having harmonic oscillator mass  20 , wall thickness, material composition, extension length and flexible cylinder discontinuities. The harmonic oscillator  15  composed of a harmonic oscillator mass  20  and a flexible cylinder extension  25  of the muzzle  9 . The harmonic oscillator  15  including harmonic oscillator mass  20  and flexible cylinder extension  25 , as depicted in FIG. 1 and 14,  14 A and  14 B, may be formed integral with the machining or other formation of the barrel  7  or may be elements affixed to the barrel  7  in the form of components distinct from the manufacture of the barrel  7 . The term ‘affixed’ used in conjunction with the harmonic oscillator  15 , including harmonic oscillator mass  20  and flexible cylinder extension  25  , includes formation integral to the manufacturing of the barrel  7  as well as the attachment of elements or components inherently separate from the barrel  7 . The harmonic oscillator  15  is tuned producing a standing wave, corresponding to the frequency of the short term vibrational response, between an inertial mass  40  and the harmonic oscillator mass  20 , that bends the barrel  7  proximal to the muzzle  9 , so that the muzzle dispersion angle is minimized. The first function of the harmonic oscillator  15  is to produce a torque, or moment, between the barrel muzzle  9  and the harmonic oscillator  15  in response to barrel  7  vibrations that bends the barrel  7  proximal to the muzzle  9  so that its dispersion angle at the muzzle  9  remains parallel with the bore axis  13 . The bore axis  13  extends from the cartridge chamber  11  to the muzzle  9  centrally positioned along the barrel bore  8 . Thus, the bullet path remains parallel to the bore axis  13  as it exits the muzzle  9 . 
     The design parameters for the tuning of the harmonic oscillator  15  are mass (harmonic oscillator mass  20 ), flexible cylinder extension wall  27  thickness and material composition, flexible cylinder extension  25  length, and flexible cylinder discontinuities  30 . Tuning may be accomplished by placement of the harmonic oscillator mass  20  and adjustment of the flexibility of the flexible cylinder extension  25 , as for example, in the vertical and horizontal directions, by adjustment of one or more of wall thickness, material composition and length of the flexible cylinder extension  25 . Flexible cylinder discontinuities  30  are composed of penetrations through the flexible cylinder extension wall  27 , grooves in the flexible cylinder extension surface  28  or other artifacts or features which change the area moment of the flexible cylinder extension  25  relative to the area moment of the barrel  9  thus changing the relative flexibility and reflecting vibrational energy. The flexible cylinder discontinuities  30  may be penetrations through the flexible cylinder extension wall  27  from the flexible extension bore  26  to the flexible cylinder extension surface  28 . 
     The depiction of the flexible cylinder extension  15  as shown in FIGS. 14,  15  and  15 A demonstrates flexible cylinder discontinuities  30  with a circular cross section. However, the function of the flexible cylinder discontinuities  30 , to adjust or increase the flexibility of the flexible cylinder extension  15  will also be served with other configurations or cross sections including slits as depicted in FIG.  14 A. The flexible cylinder discontinuities  30  may also be formed with circumferential grooves in the flexible cylinder extension  25  as shown in FIG.  14 B. The flexible cylinder extension  25  may demonstrate a flexibility different from the barrel flexibility, as determined for a particular rifle barrel by design optimization, which will be determined by a function of the combination of material composing the flexible cylinder extension  25 , the thickness of the flexible cylinder extension wall  27 , the length of the flexible cylinder extension  25  and the configuration of flexible cylinder discontinuities  30 . The second function of the harmonic oscillator mass  20  of the harmonic oscillator  15  is to provide an inertial mass at the barrel end  10  of the barrel  7  that will act in conjunction with inertial mass  40  to bend the barrel  7  between the inertial mass  40  and the muzzle  9  to be parallel to the bore axis  13  for lower frequencies such as the fundamental vibrational mode. The flexible cylinder extension  25  is affixed by means to the barrel  7  at the muzzle  9 . Means of affixing the flexible cylinder extension  25  to the barrel  7  may be through welding, a threaded attachment, other connective means or as a part of the original manufacturing process as an extension of the barrel material. 
     The harmonic oscillator mass  20  is cylindrical in the preferred embodiment having a mass bore  21  which receives the flexible cylinder extension  25  at a position most distal from the muzzle  9 . The harmonic oscillator mass  20  is not limited to a cylindrical form but may take any desired shape. The harmonic oscillator mass  20  receives and is affixed to the flexible cylinder extension  25  by means including threaded means as depicted in FIG. 15, welded means as depicted in FIG. 15A or other connective means. 
     A second component of the preferred embodiment is an inertial mass  40  having a perimeter  41  as shown as detail  8  of FIG.  1  and FIGS. 8,  8 A,  9  and  9 A. The inertial mass  40  is attached, formed or affixed to the barrel  7  at a point on the barrel  7  determined by specific analysis and design that will reduce the angular deflection of the muzzle most effectively, and preferably at a point for maximum reduction of said angle. The inertial mass  40  reduces the transmission of the short term vibrational response generated near the cartridge chamber  11  to the barrel  7  proximal the muzzle  9 . The inertial mass  40  reacts in relationship to the harmonic oscillator  15 , by bending the barrel  7  proximal the muzzle  9  reducing the dispersion angle at the muzzle  9 . The inertial mass  40 , in the preferred embodiment as shown in FIGS. 1,  8 ,  10 ,  11  and  12 , is cylindrical having a first and second end  42 ,  43  and an inertial mass axis  44  centrally positioned and passing from the first to the second end  42 ,  43 . A cylindrical inertial mass bore  46  extends from the first to the second end  42 ,  43  concentrically positioned in relation to the inertial mass axis  44 . The inertial mass bore  46  is sized to receive a rifle barrel  7  or otherwise the cantilever portion of the device addressed by the user. Alternative embodiments of the inertial mass  40  will have shapes other than cylindrical which are dictated by design and esthetic values while accomplishing the function intended. 
     The inertial mass bore  46  has an interior perimeter  48  with at least a first annulus  50  formed at the interior perimeter  48 . At least one circumferential discontinuity groove  57  is formed in the barrel surface  14  intermediate the cartridge chamber  11  and muzzle  9  positioned such that it is in pressure communication with the first annulus  50  when the inertial mass  40  is affixed at its barrel  7  position. The preferred embodiment will have a first and second annulus  50 ,  51  each forming a channel in the interior perimeter  48  circumnavigating the entirety of the interior perimeter  48  and in pressure communication with the barrel  7 . In the preferred embodiment of the invention, the barrel  7  has discontinuity apertures  55  extending from the barrel bore  8  to the barrel surface  14  at the discontinuity groove  57  providing pressure communication from the barrel bore  8  to the first annulus  50  as depicted in FIG.  10 . The at least one discontinuity groove  57  and discontinuity apertures  55  increase the barrel  7  flexibility and add to the effectiveness of the inertial mass  40  to decouple and isolate the vibrational transients, including short term vibrational transients, originating in the portion of barrel  7  proximal the cartridge chamber  11  from being transmitted to the muzzle  9 . First annulus gas ports  52  allow pressure communication from the first annulus  50  to the second annulus  51  as shown in FIG.  10 . Second annulus gas ports  53  allow pressure communication from the second annulus  51  to outside atmosphere as shown in FIG.  10 . Cartridge combustion gasses are vented, in sequence, from discontinuity apertures  55  into the first annulus  50 ; from the first annulus  50  through first annulus gas ports  52  into the second annulus  51 ; and from the second annulus  51  through second annulus gas ports  53  to outside atmosphere. An alternative embodiment will have the inertial mass  40  configured with no gas porting and hence, in this embodiment, there will be no discontinuity aperture or groove  55 ,  57 . Another alternative embodiment will have the inertial mass  40  positioned with gas porting functions in communication with at least one discontinuity aperture  55  with no discontinuity groove  57 . 
     The inertial mass  40  is affixed to the barrel  7  by means. The inertial mass  40 , as depicted in FIG. 1, may be formed integral with the machining or other formation of the barrel  7  or may be elements affixed to the barrel  7  in the form of components distinct from the manufacture of the barrel  7 . The term ‘affixed’ used in conjunction with the inertial mass  40  includes formation integral to the manufacturing of the barrel  7  as well as the attachment of elements or components inherently separate from the barrel  7 . In the preferred embodiment the inertial mass bore  46  receives a rifle barrel  7  such that either the first or second end  42 ,  43  is directed toward the muzzle  9 . Means for affixing the inertial mass  40  to the barrel  7  in the preferred embodiment, as shown in FIG. 10, is by use of a locking collar  61 . The method of retaining the inertial mass  40  in its position is shown by detail  13  in FIG. 10 in the use of a tapered split ring  59  having a beveled surface  60 , a ring gap  59 A and a spring function. The tapered split ring  59  is bound by friction against the barrel  7  by the force of a locking collar  61  having a locking collar bore  62  which bears against the beveled surface  60 . The inertial mass bore  46  bears against the beveled surface  60  with retaining bolts securing the locking collar  61  and inertial mass  40  causing the tapered split ring  59  to bind in place by friction. The inertial mass bore  46 , proximal to the first end  42 , and the locking collar  61  may have a surface beveled to receive and bear against the tapered split ring  59  beveled surface  60 . The inertial mass  40  may be affixed in position on the barrel  7  by other means including threaded means, welding, lock nuts, adhesives and other mechanical connective means. 
     The first function of the inertial mass  40  is to reduce the transmission of vibrations generated near the cartridge chamber  11  to a section of barrel  7  proximal the muzzle  9 . The inertial mass  40  in its simplest form is solely a mass as shown in FIG.  1 . The combination of inertial mass  40  with discontinuity apertures  55  and discontinuity groove  57  reflects the vibrational energy away from the section of barrel  7  proximal the muzzle  9  towards a position proximal the cartridge chamber  11  from a point intermediate the barrel muzzle  9  and the cartridge chamber  11  and thus prevents or reduces their transmission from the cartridge chamber  11  towards the muzzle  9 . A second function of the inertial mass  40 , in relationship to the harmonic oscillator  15 , is to react to a lower frequency barrel  7  vibration by bending the portion of the barrel  7  proximal the muzzle  9  to reduce the angle of dispersion at the muzzle  9 . A third function of the inertial mass  40  is to reduce gas pressure between the inertial mass  40  and muzzle  9  thus reducing the gas pressure against a bullet as it exits the muzzle  9 . Discontinuity apertures  55  from the barrel bore  8  to the barrel surface  14  in the barrel  7  port gasses out of the barrel bore  8  at the inertial mass  40  thus relieving pressure that could deflect the orientation of the bullet as it exits the barrel  7  at the muzzle  9 . A fourth function of the inertial mass  40  as configured is to reduce the pressure of the gasses ported from the barrel  7  at the second annulus gas ports  53 . The configuration of porting cartridge combustion gasses, in sequence, from discontinuity apertures  55  into the first annulus  50 ; from the first annulus  50  through first annulus gas ports  52  into the second annulus  51 ; and from the second annulus  51  through second annulus gas ports  53  to outside atmosphere is with design intent to reduce gas jets normal to the bore axis  13 . Gas jets normal to the bore axis  13  may well be unequal in their vertical and horizontal components thus deflecting the barrel. The configuration of the first and second annulus&#39;  50 ,  51  and first and second annulus gas ports  52 ,  53  will be such as to vent combustion gasses away from normal to minimize any unwanted deflection of the barrel  7 . The configuration of the inertial mass  40 , when affixed at the barrel  7 , may port combustion gasses either toward the muzzle  9  or the cartridge chamber  11 . The orientation of the inertial mass  40 , as depicted in FIG. 10 may be with the first end  42  toward the muzzle  9  or toward the cartridge chamber  11 . Pressure reduction at the second annulus gas ports  53  is realized by the annulus and gas port configuration. The configuration demonstrated in FIG. 10 will yield the following results: the collective area of the second annulus gas ports  53  is greater than the collective area of the first annulus gas ports  52 ; the collective area of the first annulus gas ports  52  is greater than the collective area of the discontinuity apertures  55 . The collective area of ports exiting an annulus are greater than the collective area of the ports entering that annulus. The combustion gasses escaping the last set of ports, shown as second annulus gas ports  53  in FIG. 10, will be directed at an angle as close to the bore axis  13  as possible. Thus, the component of forces produced by the escaping gasses normal to the barrel that would deflect the barrel are minimized. 
     The harmonic oscillator  15  is designed or tuned such that the harmonic oscillator  15  and that portion of the barrel  7  between the inertial mass  40  and the harmonic oscillator mass  20  function together as a unit so that vibrational energy transmitted past the inertial mass  40  forms a transient standing wave, between the inertial mass  40  and the harmonic oscillator mass  20 . This functionality of forming a transient standing wave is optimized so that the said standing wave has a minimized slope, and thus a minimized dispersion angle, where the harmonic oscillator  15  is attached to the muzzle  9 , for an extended window of bullet exit times. 
     A third component, shown as Detail  2  on FIG. 1, is a barrel spring suspension system  65 . This component will not be required in certain applications involving in particular larger caliber guns for military applications. The function of the spring suspension system  65  is to first provide an adjustment of the vibrational coupling boundary conditions between the barrel  7  and the rifle stock  12 . A biasing means having a spring function is secured between the barrel  7  and the rifle stock  12 . The biasing means may be spring means including leaf, coil and other spring devices. Additional biasing means providing a spring function may be provided by the use of plastic, synthetic rubber or foam materials having resilient elastomeric characteristics. The barrel spring suspension system  65 , in the preferred embodiment, is composed of a housing  70 , generally cylindrical, comprised of a lower and upper housing  73 ,  76  each semi-circular in cross section and affixed together, by means including mechanical and adhesive and provided for example, as in the preferred embodiment, by screws or bolts affixing the lower and upper housing  73 ,  76  together and to the rifle stock. The cylindrical housing  70  comprised of the lower and upper housing  73 ,  76  is composed of a rigid material provided, for example as in the preferred embodiment of metal. The barrel spring suspension system  65  housing  70  may well be composed of other rigid materials including composite materials, plastics and other rigid materials and may be of a one piece construction. The use of a lower and upper housing  73 ,  76  is for convenience in retrofitting of rifles and may not be the form preferred in an original manufacturing process. The lower and upper housing  73 ,  76  functions as the containment means, between barrel  7  and lower and upper housing  73 ,  76  for a biasing means providing a spring function or vibration coupling function between the barrel  7  and the rifle stock  12 . Containment means may take forms other than the cylindrical housing  70  presented herein and is limited only in the need of securing a biasing means between barrel  7  and stock  12 . The housing  70  is not limited to a cylindrical shape. 
     The biasing means, of the spring suspension system  65 , is provided in the preferred embodiment by at least one leaf spring  80  secured by means between the housing  70  and the barrel  7 . The biasing means may be provided by a plurality of devices having a spring function and could be provided, for example, by a plurality of leaf or coil springs. In the preferred embodiment, as shown in FIGS. 3 and 4, a set of leaf springs  80  are secured by means between the housing  70  and the barrel  7  at the barrel surface  14 . In the preferred embodiment, a set of four leaf springs  80 , which may consist of sheet metal bent in a “U” shape, are affixed by means including welding, in opposing pairs, vertically and horizontally, between the barrel  7  and housing  70 . The leaf spring  80  constants are adjusted in the vertical and horizontal directions by cutting each leaf spring  80  to the desired length. This adjustment of the vibrational coupling boundary conditions provides more control in the vibrational relationship between the barrel  7  and stock  12 . A second function of the barrel spring suspension system  65  is to provide an adjustment to the short term vibrational response of the barrel  7 . Utilization of the barrel spring suspension system  65  increases the vibrational frequency of the vibrations and more quickly defines the states of the short term vibrational response during the short time interval between powder ignition and the time the bullet leaves the muzzle  9 . In an alternative embodiment the biasing means may be provided, as shown in FIG. 6, by a coil spring  81 , affixed by means between the housing  70  and barrel  7 . 
     In addition to the rifle barrel application described herein, the principle of the harmonic oscillator, the inertial mass and barrel discontinuities, and in some applications, the barrel spring suspension system, can be applied to large military weapons that fire a single round, such as tanks, naval rifles, or large field guns, and future weapons systems such as rail guns. The vibrations in the barrels or structure that lead to inaccuracy can be controlled by the features of the rifle barrel application as they are described herein. 
     Computer simulations of the transient vibrational response (transverse displacement), in a rifle barrel  7  at a time coincident with a bullet leaving the muzzle  9  is shown in FIG.  16 . FIG. 16 is a depiction of the expected response without use of the subject invention. FIG. 17 depicts a computer simulation of the transient vibrational response (transverse displacement), with the harmonic optimization system for rifles, at a time coincident with a bullet leaving the muzzle  9 . The slope of this curve at the muzzle  9  is thus controlled to remain more parallel to the baseline bore axis  13  as compared to FIG. 16 demonstrating a reduced angular dispersion. FIG. 18 first curve  85  depicts a computer simulation, without use of the present invention, resulting in predictions of the slope of the barrel  7  at the muzzle  9  plotted against a time interval that includes the exit time of the bullet at the muzzle  9 . Curve  86  demonstrates the reduction of dispersion angle for all relevant time as the result of installation of the disclosed invention on a rifle barrel  7 . The curves  85  and  86  are proportional to the dispersion angle at the muzzle  9  as a function of time. 
     While a preferred embodiment of the present invention has been shown and described, it will be apparent to those skilled in the art that many changes and modifications may be made without departing from the invention in its broader aspects. The appended claims are therefore intended to cover all such changes and modifications as fall within the true spirit and scope of the invention.