Ball Rotor Safety and Arming Delay Device

In the accompanying drawings in which three of various embodiments of the present invention are illustrated:

FIG. 1A is a section view of a fuze applicable to 20-30 mm projectiles;

FIG. 1B is a section view along line AA of the fuze of FIG. 1A;

FIG. 2 is a cross-section view of a 40 mm shape charge grenade;

FIG. 3 is a partially sectioned view of an artillery fuze containing two safety and arming delay mechanisms.

Referring now to the drawings, a fuze containing a ball rotor safety and arming delay device constructed in accordance with the teachings of this invention is shown as 1 in FIG. 1. A ball rotor 10 is contained in a cavity in the body 19. A detonator assembly 11 is placed on the polar axis of the ball rotor 10 which in turn is placed at 80.degree. angle with respect to the spin axis to the fuze. The ball rotor is held at this angle by the firing pin 18 which is in turn held in a plastic piston 15 which is urged toward the ball rotor by spring 17. The remainder of the fuze cavity is filled with a high density fluid having a specific gravity of about 2.4. The fluid is preferably of relatively low viscosity as discussed in the above. The ball rotor 10 also contains a plastic portion 12 and a steel portion 13. This construction results in a ball rotor assembly having a polar moment of inertia which is substantially larger than the transverse moments of inertia and a density which is only slightly greater than that of the surrounding fluid. For this case, for example, the average specific gravity of the ball rotor is between 3 and 4. The effective weight of the ball rotor, in this case, therefore, is substantially less than the ball rotor used in the M505 20 mm fuze which aside from the detonator is constructed entirely of steel.

When the projectile is fired the entire fuze, and all of its parts, receive a substantial acceleration which in some cases is equal to or exceeds 100,000 g's, where g is the acceleration of gravity. This acceleration greatly increases the buoyant force on the plastic piston 15 which in fact becomes so great that the spring 17 is no longer sufficient to hold the plastic piston and the firing pin in the position shown in FIG. 1. The piston therefore moves to the front of the fuze removing the firing pin from locking the ball rotor. At the same time the projectile is experiencing a significant angular acceleration. The resulting angular velocity puts a centrifugal force on three lock balls 16 which move radially outward into groove 20. When the projectile leaves the gun and the acceleration ceases these centrifugal forces are sufficient to prevent piston 15 from moving toward the rear of the fuze.

A combination of dynamic forces arising out of the difference in the polar and transverse moments of inertia of the ball rotor and friction forces now come in to play to cause the ball rotor to move in such a way as to align its polar axis with the spin axis of the projectile. At this point the fuze is considered armed and the detonator assembly 11 is in line with the firing pin 18 and the booster 21. If the projectile strikes a target in this condition, the nose of the fuze 22 will collapse forcing piston 15 and firing pin 18 into detonator assembly 11 which explodes and initiates booster 21 which in turn sets off the high explosive in the projectile.

The friction forces play a critical role in determining the arming distance of the projectile. If no friction forces are present the ball rotor will continue indefinitely oscilating near its initial angular location with respect to the spin axis. Similarly, if the friction forces are too large, the ball can become frozen in its initial position and also never move so that its polar axis becomes aligned. The key, therefore, to understanding the operation of the ball rotor lay in a careful analysis of the friction forces coupled with the basic dynamics equations. An outline of such an analysis is provided below.

The friction forces which act on the ball result from deceleration of the projectile, static and dynamic unbalance of the projectile, unbalance of the ball rotor, precession and nutation of the projectile, and the clearance between the ball and the cavity. A careful analysis has indicated that for most projectiles the drag, nutation and precession induced forces are small. Forces arising from unbalance in the ball and from the ball socket clearance are controllable at the time of manufacture and can be made either small or large. Finally, the forces arising from static and dynamic unbalance of the shell are significant and cannot easily be eliminated at the time of manufacture. The mere act of firing a projectile itself induces eccentricities in the shell due to unequal engraving of the rotating band. It is thus these latter forces which are the major contributing factor to the variation in the total friction force acting on the ball rotor and which must be reduced both absolutely and in relation to the other friction forces and dynamic torques.

A computer solution of the dynamics equations has demonstrated that if all of the friction forces on the ball are kept small and if the shell eccentricity also is very small an exceedingly large arming distance will result. If the shell eccentricity is substantially increased, however, the arming distance will become very short if the eccentricity is located such that the ball contacts its housing at a point which coincides with a transverse axis of the ball. However, if the ball contacts its housing at a point which is 90.degree. away from the transverse axis, an exceedingly long arming distance will result. Thus, it is not only the magnitude of the shell unbalance which is important, but also its location with respect to the principle axes of inertia of the ball rotor. Since both the magnitude and location of this eccentricity cannot easily be controlled, the total friction force arising from this cause must be reduced relative to the other friction forces and dynamic torques.

In the fuze of FIG. 1, all of the friction forces have been reduced by utilizing a ball rotor which has an average density only slightly larger than that of the surrounding fluid. This fluid thus exerts a buoyant force on the ball rotor and thus substantially reduces its effective weight. All of the friction forces are proportional to the effective weight of the ball rotor and thus all of the friction forces are reduced proportionally. It has been found that a fuze designed and tested according to the above description results in substantially improved arming distance dispersion, however, the arming distance is somewhat long for the requirements of the 20-30mm. fuze. Additional computer analysis and experimentation aimed at artificially increasing one or more of the friction forces has indicated that increasing the clearance between the ball and its socket has the most favorable effect and in fact, reduces the dispersion in arming distances further and reduces the mean arming distance to meet the requirement. The nominal radial clearance in the standard M505A3 fuze is approximately 0.002 inches. In the improved fuze of FIG. 1, this clearance has been increased to approximately 0.016 inches.

The fluid used in one of a series of standard brominated fluids such as manufactured by Dow Chemical Corporation of Midland, Michigan and Halocarbon Corporation of Hackensack, New Jersey. Such fluids are available with densities ranging from one to over three. A small amount of a fatty acid has been added to this fluid to increase its boundary lubrication properties to further reduce the friction forces through reducing the coefficient of Coulomb friction. Even with the use of a lubricant, the viscous forces are negligible. The particular fatty acid used is oleic acid, however, a wide variety of boundary lubricating aditives could be used which are well known to lubrication engineers. In addition, other solid film lubricants could be applied to the surfaces of the ball or its socket to further reduce the coefficient of friction. In some applications where shorter arming times are permissible or where a larger ball could be used, the fluid could be eliminated altogether with the friction forces being reduced through the use of a solid film lubricant such as Teflon, molybdenum disulfide or graphite. In such cases, the same principles which are described herein would apply wherein the uncontrollable friction torques are reduced in comparison to the dynamic torques.

In many applications it is desirable to practice this invention without resorting to the use of a liquid. In such cases a film of solid lubricant has been successful alone. In early attempts using a very thin coating of powdered graphite, inconclusive results were obtained and these test efforts were abandoned. Extensive testing has since revealed that the solid film lubricant must be applied in a coating with a significant film thickness. It has been found that to achieve the results of this invention, that the film thickness must be at least 0.0001 inches.

A second preferred embodiment constructed in accordance with the teachings of this invention applied to a 40mm. shape charge grenade is shown at 100 in FIG. 2. The operation of this ball rotor safety and arming delay device is similar to the one described above. Upon setback the firing pin assembly 110 moves to the front of the fuze due to buoyant forces from the fluid 111 removing the firing pin 112 from the ball rotor 113. In this fuze a second spin lock ring 114 has been provided to add an additional safety feature to the fuze. After setback, this ring moves outward into a recess 115 in the housing 116 due to centrifugal forces. When the firing pin 112 and spin lock 114 are removed, the ball rotor 113 rotates into alignment under the friction forces described above. In this fuze once again fluid has been used to reduce the effective weight of the ball rotor without effecting its moments of inertia, thus all friction forces are reduced while the dynamic torques remain the same. Once again a larger clearance has been used to provide a controllable friction force. In this case, the clearance is somewhat larger in order to reduce the arming distance to the desired value.

A fuze constructed utilizing a safety and arming delay device according to the teachings of the present invention applied to artillery is illustrated at 201 in FIG. 3. Two safety and arming delay devices shown generally at 202 and 203 are utilized in a redundant fashion in this fuze. The operation of the arming portion of the safety and arming delay device is similar to that described above. Upon experiencing setback acceleration, firing pin assembly 204 moves upward until lock ball 205 is forced into groove 206 by a combination of setback and spin forces. This releases ball rotor 207 which rotates into alignment in the manner similar to that described above. This fuze provides the additional feature of a super quick or delay setting by rotating plug 230. In the position shown in FIG. 3, the fuze is set for delay operation. In this case when the projectile strikes the target, impact mass 210 moves toward the front of the fuze until lock ring 211 reaches lock ring groove 212 at which time it moves radially out of lock ring groove 213. At the cessation of the impact deceleration, impact mass spring 214 propels the impact mass 210, and thus the firing pin 216, toward the aligned detonator 215. The firing pin strikes the detonator which explodes into the booster 217 which ignites the larger boosters 218 and 219 respectively and in such a manner sets off the high explosive in the artillery shell.

If the setting plug 230 is rotated 90.degree. prior to firing of the projectile, pin 231 becomes aligned with a parallel slot (not shown) such that upon impact plunger 232 is driven through end 233 of the safety and arming delay device 202 and drives the impact mass and firing pin combination toward the detonator 215 setting off the round in the manner described above.

Two safety and arming delay devices have been used in this third example which illustrates the fact that when the friction forces can be controlled in ball rotor fuzing, the size of the safety and arming delay device can be made sufficiently small to permit redundant use of the device within a single fuze. In the fuze illustrated in FIG. 3, the safety and arming delay device 203 will fire in the delay mode regardless of the setting of the fuze. It thus serves as a redundant backup for the main safety and arming delay device 202.

In some cases if the shell eccentricities are controlled, it would be possible to even eliminate the need for the density reducing plastic used in the ball described in FIG. 1. For such a case, low friction coefficients could be achieved by utilizing a careful choice of materials on the surfaces of the ball and its cavity.

For most cases studied the preferrable controllable friction force has proven to be the clearance between the ball and its cavity. The other controllable friction force would be the unbalance in the ball rotor which could be controlled by removing portions of the ball to displace the center of mass of the ball from its geometric center. The eccentricity of the entire safety and arming delay device could of course be increased which would have the same effect as shell eccentricity, however, its magnitude and location could be controlled and thus not subject to variation from round to round. For all of the cases studied however, this other controllable friction force has not resulted in as tight a dispersion as achievable through increasing the ball socket clearance. It has resulted however, in an improvement in the arming distance dispersion over the standard ball rotor fuzes utilized to date.

In this application a somewhat longer arming distance has been achieved by supporting the ball rotor on a small support 240. This reduces the friction torques which normally brings the ball up to the projectile angular velocity at setback. In this case, therefore, the angular velocity of the ball is substantially below that of the projectile when the projectile leaves the muzzle of the gun. A computer analysis has shown that the ball rotor does not begin to align until it reaches the same angular velocity as the projectile. In this fuze the arming distance was approximately doubled by this technique. The presence of the fluid between the ball and its housing delays the spin-up of the ball due to hydrodynamic bearing forces arising from the relative rotation of the ball and socket. The housing of course could be designed to maximize or minimize this effect by those skilled in the art of hydrodynamic bearing design.

In other applications such as that shown in FIG. 1, the arming distance would be too long if the ball does not achieve a significant portion of the projectile angular velocity. For this case therefore a tab 50 (see FIG. 2) has been provided to lock the ball to the shell during setback. This tab 50 is removed by centrifugal forces after the ball has achieved a significant angular velocity.

The mathematical analysis of the ball rotor can be carried out by those skilled in computer programming and dynamics analysis. The basic equations to be solved are the Eular equations as presented in Goldstein, H., Classical Mechanics, Chapter 4-5. Reading: Addison Welsley, 1950. These equations can be integrated in a time step simulation type analysis utilizing, for example, numerical techniques described in Ralston, A., A First Course in Numerical Analysis, Chapter 5. New York: McGraw-Hill Inc., 1965.

Thus the numerous aforementioned objects and advantages among others are most effectively obtained. Although several preferred embodiments and applications have been described, discussed, illustrated above it should be understood that this invention is in no sense limited thereby but its scope is to be determined by that of the appended claims.