PROGRAMMED SHELL CASING EJECTOR APPARATUS FOR AUTOMATIC CANNON

Abstract: Programmed shell casing ejector apparatus (10), for an automatic cannon (18), includes an ejector member (14) axially slidably mounted to an axially reciprocating bolt assembly (24), a pair of cam tracks (12) symmetrically fixed to a cannon mount (36) and a pair of cam track followers (16) pivotally mounted to the bolt assembly (24) to engage the ejector member (14) and, when the bolt assembly recoils after firing, also to engage the cam tracks (12). Ejection of a shell casing (180), held to a bolt face (80) by an extractor (84) occurs when the ejector member (14) is moved forwardly, relative to the recoiling bolt assembly (24), by the cam track followers (16) sliding along the cam tracks (12). Casing ejection timing and velocity is programmed to prevent cannon malfunction due to improper ejection, by relatively configuring the cam tracks (12) and followers (16) so that the ejector member (14) moves forwardly relative to the bolt assembly (24) at a controlled, increasing ejection velocity which is substantially less than bolt recoil velocity.

Description: PROGRAMMED SHELL CASING EJECTOR APPARATUS FOR AUTOMATIC CANNON Technical Field The present invention relates to fired shell casing ejectors for automatic cannon and the like, and more particularly to types of such ejectors which substantially reduce ejector-casing impact damage and prevent erratic and unpredictable casing ejection.. Background Art Fast firing rates and very reliable operation are both essential for automatic cannon used in such critical applications as close-in air defense weapon systems. In attempting to attain high target hit probabilities, cannon performance improvements are continually necessary to adapt the systems to in¬ creasingly faster and more sophisticated aircraft targets which afford only brief tracking, ' and hence firing, times. Close-in air defense weapons systems typically use a pair of single barrel, gas operated automatic cannon of 3Q-40τπm calibre. In such cannon, barrel gas pressure caused by firing is used to unlock a bolt assembly from the breech and drive both the bolt assembly and the just fired shell casing rearwardly towards a recoil buffer. During this recoil, an ejector apparatus causes the empty casing to be ejected from the cannon. The buffer stops bolt assembly recoil, and counterrecoils the assembly back towards the breech. On passing a shell supply port, a live or unfired shell is picked up by the counter- recoiling bolt assembly and driven fσrwardly into the breech for firing. - O P! / P 0 Firing rates of this type cannon are determined by bolt assembly cycling times, increased firing rates being generally achieved by reducing the cycling time. This is typically done by shortening the bolt assembly travel p th between the breech and the buffer and/or by increasing average bolt assembly velocity over the cycling path. In practice, however, many interrelated design problems must be overcome to increase the firing rate 0 by even a small amount. As an illustration, when bolt velocities are increased, such problems are encountered as exces * sive mechanical stresses, reduced recoil buffer efficiencies, improper shell feeding and erratic shell casing ejection after firing. Solving any one of these -5 problems may introduce or increase the magnitude of other problems. Addressing specifically the casing ejection problems, as bolt recoil velocity is increased to in¬ crease firing rates, reliable and predictable shell ej.ect- 0 ion becomes very difficult, particularly in cannon m which the casings are relatively heavy. This difficulty causes faulty or unpredictable ejections which cause jammings or other cannon malfunctions. Typically, a casing ejector assembly includes a -5 bolt mounted ejector member which, as the bolt assembly recoils past an ejection port, pushes the shell casing away from the bolt towards the port in response to the ejector member impacting a fixed part of the cannon. When the bolt travel path is made very short to 0 decrease bolt cycling time, the ejector port must also be shortened and must be positioned relatively near the recoil buffer. As a result, shell casings not only have a small opening through which they must be ejected, but also must be ejected sufficiently rapidly to avoid 5 being hit by the bolt on counterrecoil. As a result, -fcUREAlT 0MP1 ejected casings tend to hit edges of the port and bounce back into the gun. Furthermore, because of substantial recoil momentum of heavy shell casings, an abruptly stopped • 5 ejector member tends to cause considerable impact damage to the casings. Thus, at high casing recoil velocities, fragments punched by the ejector member from the impacted casing rim may be driven and lodge in parts of the cannon causing jamming or other mal- • *-0 functions of the cannon. Alternatively, the ejector pin may deform the casing as the casing is pushed away from the bolt to such an extent that considerable ejection energy is lost. Consequently, ejection may be slow and the casing may not fully eject before the bolt •1 -5 assembly returns to the ejection position and the casing may be kicked back into the cannon to cause jamming. Thus, as firing rates are increased by in¬ creasing bolt assembly recoil velocity and decreasing bolt assembly path length, malfunctions of the cannon 0 attributable to faulty casing ejection also increase. B • *e»cause of the problems associated with ejecting relatively heavy shell casings, some large automatic cannon employ mechanical spring-type ejector buffers 'in attempts to reduce impact damage to the casings and *5 thereby provide controlled ejection thereof. However, as is generally known, operaion of mechanical springs at high impact velocities is unpredictable because separate coils or portions of the springs tend to function independently. Also at very high velocity 0 impact, heavy mechanical springs tend not to behave as a spring but as a non-compliant structure, Hence, undesirable rim punching or deformation may still occur and casing ejection is still erratic and uncontrolled. For these and other reasons, improvements to shell casing ejection apparatus are required before firing rates of large automatic cannon can be substantially in¬ creased and before operational reliability even at existing firing rates can be significantly improved. Disclosure of Invention Thus, and particularly adapted for use in an automatic cannon or the like having an axially reciprocating bolt assembly with means for holding, after firing of the cannon, a fired shell casing to a forward face thereof, and having a shell ejection port located along the path of bolt assembly recipro¬ cating travel, a programmed shell casing ejector, according to the present invention, comprises an ejector member having a shell base engaging portion and an actuation portion and means for mounting the ejector member to the bolt assembly for longitudinal movement relative thereto. Also included in the ejection apparatus are nόn-compliant camming means for causing, as the bolt assembly travels rearwardly after firing of the cannon, the ejector member to move forwardly relative to the bolt assembly at a controlled and increasing velocity which is substantially less than rearward velocity of the bolt assembly, Accordingly, fired shell casings held to the bolt assembly face are impacted by the ejector member without significant impact damage and are hence ejected outwardly through the ejection port in a highly predictable and consistent manner. More specifically, the camming means includes a pair of cam tracks and a corresponding pair of cam track followers. The cam tracks are symmetrically mounted to portions of the cannon which do not reciprocate with the bolt assembly, and are formed to provide a pair of laterally spaced apart camming surfaces having generally parallel, laterally spaced apart forward regions and generally parallel rearward 5 regions which are laterally spaced more closely to¬ gether than are the forward regions. Inwardly con¬ verging intermediate regions of the camming surfaces interconnect the forward and rearward regions thereof. Pivotally mounted to the bolt assembly, also in 0 symmetrical manner, the cam followers each have a first, ejector member engaging portion and a second portion which engages a corresponding one of the camming surfaces when the bolt assembly, recoils- towards a casing ejection position. *5 Configuration of the camming surfaces intermediate regions is such as to cause, as the bolt assembly re¬ coils rearwardly, the cam follower second portions to . remain in engagement with such camming surface regions without bouncing. As the cam follower second portions 0 move along the camming surface intermediate regions, the cam followers are caused to pivot about mounting axes on the bolt carrier. This cam follower pivoting causes the cam follower second portions to move the ejector member shell base engaging portion forwardly, 5 relative to the bolt assembly, from a first position, in which the ejector member shell base engaging portion does not extend forwardly of the bolt assembly forward face, to a second position, in which the engaging portion projects substantially forwardly of the bolt 0 assembly face to engage, and hence cause ejection of, a fired shell casing. A shell base engaging face of the ejector member is formed in wedge shape to have edge contact with the shell casing .base. This ejection member edge cuts slightly into the casing base to present slipping up of the casing during ejection. Pivotally mounted to a forward region of the ejector member is a shell pick up element adapted for engaging a base portion of an unfired shell at a shell loading position upon forward movement of the bolt assembly therepast and for thereby stripping the shell forwardly from the loading position to enable shell loading and firing. The pick up element pivots between an extended, shell pick up position and a retracted, shell clearance position. Biasing means urge the element to the pick up position while permitting movement to the retracted position so that the bolt assembly can move rearwardly beneath a shell in the loading position. Sloped upper regions of the ejector member casing engaging surface function as a ramp to guide the base of the picked up shell down¬ wardly towards a barrel bore axis. Brief Description of the Drawings A better understanding of the present invention may be had from a consideration of the following detailed description, taking in conjunction with the accompany¬ ing drawings in which: Figure 1 is a partially cutaway perspective view of an automatic cannon having associated therewith a programmed ejector apparatus according to the present invention; Figure 2 is a detailed perspective view of the bolt assembly of Figure 1, showing portions of the programmed ejector apparatus including an ejector member slidably mounted on the bolt assembly and a pair of cam track followers pivotally mounted to the bolt assembly; Figure 3 is an exploded view of the assembly of Figure 2, showing features of the ejector member and cam followers and related portions of the bolt assembly; Figure 4 is a broken away perspective view, •5 showing cam track portions of the ejector apparatus fixed to an associated cannon mount and having a pair of laterally spaced, contoured camming surfaces of the cam track portions for guiding the cam followers; Figure 5 is an outline representation of the cam 0 track follower showing the sequential or stepwise manner in which camming surfaces contour is determined and constructed; Figure 6 is a graph in which is plotted angle of rotation of the cam track followers as a function of -5 axial movement of the followers relative to the cam tracks; Figure 7 is a plan view, partially in horizontal cross section, of the assembly of Figure 2 with the cam tracks added, showing the shell ejector cam followers 0 inside forward portions of the cam tracks, and also showing a pair of springs and push rods which bias a shell pick up element mounted to the ejector member; Figure 8 is a plan view, similar to Figure 7 but at an instant later, showing the cam followers en- *5 gaging intermediate, inwardly converging regions of the camming surfaces and consequent pivoting of the cam followers to cause initial forward extending of the ejector member past a forward bolt face to initiate shell casing ejection; 0 Figure 9 is a plan view, similar to Figure 8, but at an instant later, showing the cam followers now moving along rearward regions of the camming surfaces with consequent complete pivoting of the cam followers and forward extension of the ejector member relative to the bolt assembly, and showing the shell casing as it is driven away from the bolt assembly; Figure 10 is an elevational view, in cross section, corresponding in time to Figure 9, showing the cam followers along the rearward camming surface regions, complete forward extension of the ejector member and a shell casing being ejected downwardly through the ejection port; Figure 11 is a vertical sectional view, showing an 0 ejector member mounted shell pick up element in a re¬ tracted position enabling recoil movement of the bolt assembly under an unfired shell in a loading position; and, Figure 12 is a vertical sectional view, showing -5 the shell pick up element in a position for engaging and stripping an unfired shell from the shell loading position as the bolt assembly moves forwardly in counterrecoil. 0 Best Mode of Carrying Out Invention As seen in Figure 1, a programmed shell casing ejector apparatus 10, according to the present invention, comprises generally a laterally spaced pair of cam tracks 12, an ejector member 14 and a pair of cam -5 followers 16 which cooperate with the cam tracks to operate the ejector member, as more particularly described below. Also shown in Figure 1, for illustrative purposes, is an automatic cannon 18 with which the ejector 0 apparatus 10 is operatively associated. Although the cannon 18 may be virtually any type of automatic cannon or gun which operates on an axially reciprocating bolt principle, the particular cannon shown is of the open- framework receiver type described in U.S. Patent 5 application, Serial No. 24,186 , filed on even date herewith. Pertinent parts of the cannon 18, that is, " those parts associated in some manner with operation of the ejector apparatus, include a bolt assembly 24 to which the ejector member 14 and cam followers 16 are mounted, a combination bolt recoil and sear buffer 26 and a breech ring 28 ~ . Guiding reciprocating movement of the bolt assembly 24 between the breech ring 28 and the buffer 26 is a laterally spaced apart pair of support tubes 30 which also mount the buffer relative to the breech ring. Further guiding and support of the bolt assembly 24 is provided by a plate 32 which extends between the breech ring 28 and buffer 26 and which is formed having an axially elongated shell casing ejection port 34. The cannon 18 is mounted to mounting means 36, to which the cam tracks 12 are fixed, in a symmetrical manner about a bore axis 42 of a cannon barrel 44, as more particularly described below. More particularly, as seen in Figures 2 and 3 (which show the bolt assembly 24 in assembled and exploded form), the ejector member 12, formed generally in axially elongate bar form with a rectangular cross- section, has a rearward, actuation portion 46 and a for¬ ward, shell casing engaging portion 48. To enable mounting of a shell pick up element 50, for below described purposes, the ejector member shell engaging portion 48 is formed having a pair of laterally spaced, forwardly projecting ears 52. Formed on a forward end of each of the ears 52 is a wedge shaped surface com- prising an upper surface region 54 and a lower surface region 56 which are slanted rearwardly to define an intersection or-impact edge 58. During ejection impact, as more fully described below, the casing line contact by the edge 58 maintains appropriate casing position during at least initial ejection stages. As seen in Figures 2 and 3, the bolt assembly 24, to which the ejector member 14 and cam followers are mounted, comprises ' generally an elongate, "L" shaped bolt 60, to a rearwardly extending portion 62 of which is mounted, for axial sliding movement relative thereto, a "T" shaped bolt carrier 64. Pivotally mounted to the rearwardly extending bolt portion 62 is a pair of bolt-breech ring locking lugs 68. Pivotal lug axes 70, which are in vertical planes to each side of the assembled carrier 64 and orthogonal to the barrel bore axis 42, also form pivotal axes for the cam followers 16, as described below. Included in a bolt forward portion 78, at a forward face 80 thereof, is a downwardly extending shell base receiving recess 82, a lower region of which communicates with a generally conventional shell casing extractor 84. Such extractor 84 in addition to assisting shell casing extraction from the breech ring 28 also holds an extracted shell casing in the recess 82 and to the bolt face 80 until ejection. In addition and importantly, the extractor 84 provides a pivoting point for the shell casing during the below described operation. Mounting of the ejector member 14 to the bolt assembly 24, for required axial sliding movement relative thereto, is enabled by a pair of longitudinal lugs or rails 90 formed along lower outer regions of the ears 52 in a symmetrical manner. To receive the shell casing engaging portion 48 of the member 14, including the ears 52 and the rails 90, a longitudinal T-shaped slot 92 is formed downwardly into the bolt forward portion 78 from an upper surface 94 thereof, about a vertical plane of symmetry through the bore axis 42. Side regions 96 of the slot 92 are con¬ figured for receiving the ejector member rails 90. Longitudinal movement of the ejector member 14, relative to the holt assembly 24, is further guided by an elongate slot 98 formed downwardly into the bolt carrier 64 from an upper surface 100 thereof. On assembly, lower rearward regions of the ejector member are received downwardly into such slot 98. During ejector operation, the bolt slot 92 and the bolt carrier slot 98 guide movement of the ejector member 14 between a first, rearward position, relative to the bolt assembly 24, in whch the ejector-casing impact edges 58 is flush with, or slightly rearwardly of, the bolt face 80 and a second, forwardmost ejection position in which such impact edges is substantially forwardly of the bolt face, as more particularly described below. To prevent impact absorbing damage, other than that necessary to maintain casing alignment, to bases of shell casings being e ected by the ejector member 14, and to enable consistent and predictable casing ejection through the ejection port 34, the cam tracks 12 and cam followers 16 are configured to move the ejector member forwardly, relative to the recoiling bolt assembly, from the first to the second positions in a precisely predetermined and controlled manner. It should be understood that although for ease and clarity of description the ejector member 14 is herein generally described as being moved forwardly (towards the breech ring 28) relative to the bolt assembly 24, what actually occurs is that the bolt assembly moves rearwardly relative to the ejector member. That is, after firing, the bolt assembly 24, the- ejector member 14 and an extracted shell casing are all recoiled rearwardly towards the buffer 26 together at the same velocity. At an ejection position the ejector member 14 is slowed down in a controlled manner so that the bolt assemly moves rearwardly at greater velocity beneath the member. Consequently the member 14 "moves forwardly" beyond the bolt face 80 to cause shell casing ejection. By providing cam controlled or "programmed" slowing of the ejector member 14 during ejection, forward velocity of the ejector member relative to the bolt assembly 24 can be preprogrammed, by appropriate design of the cam tracks 12 and cam followers 16, in substantially any manner required to achieve con¬ sistently good casing ejection for the particular type cannon involved. As an example, for the particular type cannon 18 illustrated, it has been found by actual firing that consistently good casing ejection is attained by constructing the cam followers 16 and the cam tracks 12 in a manner causing forward velocity of the ejector member 14, relative to the bolt assembly 24, to be substantially less than bolt assembly recoil velocity. In consequence, impact forces between the ejector member 14 and shell casings to be ejected are greatly reduced over those which would occur if recoil movement of the ejector member were abruptly stopped. Erratic and incomplete casing ejection as well as malfunctions caused by punched out casing particles are thus virtually eliminated. Consistent shell casing ejection is further assured by relatively configuring the cam tracks 12 and the cam followers 16 so that no bouncing therebetween occurs during casing ejection. Eliminating such bouncing, by causing increasingly greater cam follower rotational velocity during casing ejection, with consequently increasing forward relative velocity of the ejector member 14 substantially reduces cam track and follower wear which, as extent of damage increases, would adversely affect casing ejection. Since relative forward movement of the ejection member 14 is caused by the cam followers 16 moving rearwardly along the cam tracks 12, rearward velocity of the cam follower pivotal axes 70 relative to the cam tracks is an important factor in determining cam follower and track configurations. However this realtive rearward velocity of the cam follower axes 70 depends not only upon recoil velocity of the bolt 60 to which the cam followers 16 are pivotally mounted but also upon any other relative movement between the bolt and the cam tracks 12 during ejection. Con¬ sequently, unless the cam tracks 12 are mounted directly onto the cannon 18, recoil and/or counter- recoil velocity of the cannon at the time of casing, ejection will add to, or subtract from, bolt assembly recoil velocity. This effect must be considered in determining relative velocity between the cam follower axes 70 and the cam tracks 12 for configuration design purposes, as described below. Configuration of the cam followers 16 is determined, in part, by configuration of the bolt 60 or the bolt assembly 24, location of the pivotal axes 70, con¬ figuration of the ejector member 14 and constraints on locating the cam tracks 12. This follows from the requirement that the cam followers 16 must engage the cam tracks 12 and the ejector member 14 during casing ejection. For the particular type of bolt assembly 24 illustrated, in which the bolt carrier 64 slides for¬ wardly relative to the bolt 60 to move the locking lugs 68 out into mating breech ring recesses 104 (Figure 1) , and to cause shell firing by a firing pin 106, the cam followers 16 are generally triangular in outline (Figures 2 and 3). Each cam follower 16 has a first, ejector member engaging arm 108 which is directed generally inwardly towards the barrel bore axis 42 when the engaged ejector member 14 is in the first, rearward position (Figure 2). Each of the first arms 108 is formed having an outwardly and forwardly directed ejector member actuation face 110. Corresponding outwardly opening, rectangular recesses 112, formed on opposite sides of the ejector member actuation portion 46, receive inwardly projecting ends of the cam follower first arms 108. A vertical mounting aperture 114, formed generally centrally through each of the cam followers 16, enables mounting of the followers on cylindrical studs 116 projecting upwardly from upper surfaces 118 of the locking lugs 68. In this manner, the cam followers 16 and the locking lugs 68 have common pivotal axes 70. Rearward travel of the ejector member 14 is limited by abutting surfaces 120 on the cam followers 16 forwardly of the first arms 108 and corresponding side surface regions 122 on the ejector member actuation portion 46 forwardly of the recesses 112. Engagement between the cam followers 16 and the cam tracks 12 is enabled by a rearwardly and outwardly projecting second, cam track engaging arm 128 of generally triangular shape on each of the cam followers. Arcuate cam track engaging surfaces 130 are formed at outer ends of the second arms 128. As previously mentioned, exact configuration, including length of the first and second cam follower arms 108 and 128 depend upon relative mounting location of the cam tracks 12, the followers 16 and the ejector member 14 as well as required casing ejection characteristics. Referring to Figure 4, it can be seen that the cam tracks 12 are fixed to the cannon mounting means 36 by a pair of longitudinally spaced apart, transverse brackets 136 which are in turn fixed to the mounting means by bolts 138. For the type of cannon 18 illustrated, the brackets 136 may support other portions related to the cannon, such as a trigger module (not shown) , in operative relationship therewith. Mounting is such that the cam tracks 12 are symmetrical about the barrel bore axes 42 and in a common plane thereabove. Each of the cam tracks 12, which are axially elongate plates, have an inwardly (towards the bore axis 42) facing camming surface 140 positioned for engagement by a corresponding cam follower second arm surface 130 as the bolt assembly 24 recoils into casing ejection position. The opposing camming surfaces 140 are divided for purposes of description into forward, intermediate and rearward regions 142, 144, and 146, respectively. Lateral spacing between the camming surface forward regions 142 is equal to, or slightly greater than, the distance between outermost regions of the cam follower surfaces 130 when the engaged ejector member 14 is in the first, rearward position. In this position, the cam followers 16 are in an extended rotational position. To allow for tolerances, wear and slight misalignments, the opposing camming surface regions 142 may be slightly forwardly diverging so that the cam followers 16 may enter the cam tracks 12 without interference. Lateral separation of the parallel and opposing camming surface rearward regions 146 is substantially less than that of the forward regions 142. Such rear¬ ward separation is equal to lateral distance between 16 outermost regions of the cam follower surfaces 130 with the engaged ejector member 14 in the second, forwardmost position relative to the bolt assembly 24; that is, when the cam followers 16 are pivoted to a retracted position. Length of the camming surface rearward regions 146, which extend rearwardly into proximity with the buffer 26, is sufficient to maintain the cam followers 16 in the retracted position during remaining bolt assembly recoil and until the bolt assembly 24 approaches a shell pick up position on counterrecoil. Thus, complete pivotal movement of the cam followers 16 from the extended to the retracted positions, with consequent relative forward ejection movement of the ejector member 14 from the first to the second positions is caused as the cam follower second arm surfaces 130 rearwardly traverse the camming surface regions 144. Such camming surface regions 144 are accordingly configured to cause the required ejector member movement relative to the bolt assembly 24 and to prevent bouncing between the cam follower surfaces 130 and the surface regions 144. As is shown in Figure 5, contour of the camming surface intermediate regions 144, shown rearwardly extending between points "A" and "B", is established by plotting sequential rotational positions of the cam follower surfaces 130 (only one cam follower 16 being shown because of symmetry) as the cam follower axes 70 move rearwardly. As such axes 70 recoil in the direction of Arrow "C", the cam followers 16 are caused, by engagement between the cam follower surfaces 130 and the camming surface intermediate regions 144, to pivot inwardly in the direction of Arrow "D". To lay out OMPI ' /?N T\ the surface region 144, for each equal increment of rearward axes movement, "1", the cam follower is rotated a slightly greater angle in the direction of Arrow "D". A sequence of rotational positions of the surface 130 - positions 130a, 130b, 130c ... 130n - being thereby obtained. After such layout is complete, a smooth curve is drawn tangent to the surfaces 130, 130a, 130b ... 130n to define the surface region 144. Figure 6 plots rotational angle of the cam followers 16 as a function of rearward displacement of the axes 70 in increments of "1" for the corres¬ ponding, exemplary layout of Figure 5. Starting with 0° of cam follower rotation at zero "1", at 5 "1" the cam follower has been rotated through approximately 3°; at 10 "1", through about 8°; at 15 "1", through about 18° and at 20 "1" (representing complete rotational movement of the cam followers to cause shell ejection), through about 30°. This increasing angular displacement of the cam followers 16, which is clearly evident from Figure 6, is consistent with the requirement that the cam followers are caused to pivot at increasing rotational velocity to maintain cam follower/cam track engagement without bouncing therebetween. In the above described manner, the intermediate camming surface region 144 can be layed out for virtually any reasonable configuration of the cam followers 16, bolt assembly 24 and so forth, to provide required ejector member movement relative to the asso¬ ciated bolt assembly. Other variables-,.which may require consideration in particular instances include shell casing weight, ejection port length and location, bolt assembly recoil and counterrecoil velocities and cannon recoil characteristics. Use is also made of the ejector member 14 for mounting the shell pick up element 50 (Figures 2 and 3). A spaced apart pair of rearwardly extending ears 156 of the pick up element 50 are pivotally mounted to 5 the ejector member ears 52 and an intermediate ejector member ear 158, by a pivot pin 160. Such mounting enables the element 50 to pivot between an upwardly extended, shell pick up position (shown in Figures 2 and 3) and a retracted position wherein an upper 1 surface 164 of the element is flush with an upper surface 166 of the ejector member 14. A pair of longitudinally extending springs 170 (Figure 7) , through plungers 172, urge or bias the pick up element 50 to the extended pick up position while permitting the 1 * element to be depressed downwardly to the retracted position during recoil. Function of the extended pick up element 50 is to strip, on bolt assembly counterrecoil from the buffer 26, above-the-bolt positioned shells from a feeder 20 (not shown) . Unfired shells are so positioned to be above the recoil path of the bolt assembly 24 and an extracted shell casing, assuming as is generally the case, that the shells may be moved to the feed position before ejection and recoil is complete. With the -5 pick up element 50 retracted in response to engagement with a shell in the feed position, the bolt assembly 24 and the ejector member 14 can recoil beneath the shell without significant interference. Alternatively, to avoid necessity for the pick up 3 element 50, a shell to be fed could be dropped or pushed downwardly into the counterrecoil path of the bolt assembly 24 after full recoil thereof. However for fast firing cannon, the extremely short time interval between when the bolt assembly recoils byeond the shell ^^ and when the bolt assembly must pick up the shell on counterrecoil is too short for reliably moving a shell into the bolt assembly path. As a result, either shells are often moved down too soon and interfere with bolt assembly recoil and shell casing ejection or too late to be picked up. In addition to providing convenient, exposed mounting for the pick up element 50, it is also to be appreciated that with suitable relative arrange¬ ment of the ejection apparatus 10 and shell feed portions of the cannon 18, the ejector member 14 can also be adapted for providing relatively "soft" shell pick up for some types of cannon. Soft shell pick up may be necessary to prevent shell impact damage and premature firing. To this end, it should be observed that if the cam followers 16 are still in engagement with the intermediate camming surface regions 144 during shell pick up, the ejector member 14, and hence the pick up element 50, move rearwardly relative to the bolt assembly. Accordingly, for such a cannon configuration, the result is that the pick up element 50 impacts a shell at a velocity substantially less than bolt counterrecoil velocity. Operation of the Programmed Shell Casing Ejector Apparatus 10: Operation of the ejection apparatus 10 is generally apparent from the foregoing description. However, for illustrative purposes, several time interval steps in the shell casing ejection portion of the bolt assembly recoil/counterrecoil cycle are illustrated in Figures 7-10. In Figure 7 bolt assembly 24 is shown recoiling rearwardly (Arrow "C") after firing of the cannon, a base 178 of a fired shell casing 180 being held to the bolt face 80 by the extractor 84 (not shown) . At the JUREATT OMPI W1PO - 20 instant of Figure 7, the cam followers 16 will have entered between the cam tracks 12, with the engage¬ ment arm surfaces 130 engaging the camming surface forward regions 142 forwardly of points "A" where the intermediate camming surface regions 144 start. At this instant, the cam followers 16 are still in a fully extended position with the ejector member 14 in the first, non-ejecting position and with the engagement e-ds-e 58 flush with, or slightly rearwardly of, the bolt face 80. Velocity of the ejector member 14 relative to the bolt assembly 24 is zero. That is, both are recoiling at the same velocity and ejection of the shell casing 180 has not been initiated. At the later instant of time depicted in Figure 8, the cam follower first arm surfaces 130 have engaged, and are moving rearwardly along the camming surface intermediate regions 144. As a result of the con¬ vergence of such camming surface regions 144, the cam followers 16 are caused to rotate (in the direction of Arrow "D") about the axes 70 to an intermediate position depicted. In response thereto, the ejector member 14 is moved forwardly (direction of Arrow "E") relative to the bolt assembly 24 into ejection engagement with the shell casing base 178. In this intermediate ejection position, the ejector member engaging edge 58 is forwardly of the bolt face 80 and, due to cutting slightly into the casing base 178, prevents the casing base from slipping upwardly out of full engagement by the extractor 84. Ejection rotation (direction of Arrow "F", Figure 10) of the shell casing 180 about a . hinge line created by the extractor 84 and through the ejection port 34 has started. When the rearwardly traveling cam follower surfaces 130 pass point "B" on the camming surfaces 140 and start traversing the rearward regions 146 thereof (Figures 9 and 10) the cam followers 16 have 5 been fully rotated or retracted inwardly. As a result, the ejector member 14 has been moved fully forwardly relative to the bolt assembly 24 (to the second position) and is again moving rearwardly at bolt recoil velocity. 10 However, rotational momentum already imparted to the shell casing 180 causes the casing to continue pivoting (Arrow "F" Figure 10) abouf the extractor 84 and downwardly out through the bottom plate ejection port 34. As the casing 180 continues to 15 rotate out through the port 34, the casing disengages from the extractor 84, which is spring loaded to permit pivotal movement, and is freely ejected from the cannon 18. For illustrative purposes, a free traveling ejected casing 180a is shown in phantom lines 20 i n Figure 10. It is evident that since the camming action between the cam followers 16 and the cam tracks 12 relatively gradually slows recoil movement of the ej ctor member 14 relative to the casing 180, casing impact damage, ^-^ including punching out portions of the shell casing base 178, is virtually eliminated. "Softness" of the casing ejection can, for example, be varied by varying length and convergence angle ot the camming surface intermediate regions 144. However, as 30 length of the surface regions 144 is increased to provide softer casing ejection, ejection requires more time and the bolt assembly recoil path must be correspondingly lengthened thereby increasing cycling time and reducing firing rate. But to compensate for this, to maintain a given firing rate, recoil velocities must be in¬ creased, which in turn raises ejection impact. Thus, various trade offs are ordinarily required in con¬ figuring the apparatus 10. Operation of the shell pick up element 50 is illustrated in Figures 11 and 12. In Figure 11, the bolt assembly 24, the ejector member 14 and the ex¬ tracted shell casing 180 are shown recoiling (direction of Arrow "C") together towards a shell ejection position. As the bolt assembly 24 recoils rearwardly under an unfired shell 186 located in an above-the-bolt feed position, the pick up element 50 is pushed down¬ wardly.by the shell against the springs 170 (not shown in Figures 11 and 12) to a flush, retracted position. Thus, the upper surface 164 of the pick up element 50 slides along an under side of the shell 186. However, as soon as the element 50 recoils to a position rearwardly of a base portion 190 of the shell 186, the springs 170 pivot the element upwardly to a fully extended, pick up position, (direction of Arrow "G", Figure 12). In Figure 12, the bolt assembly 24 with the ejector member 14 is shown an instant later in counterrecoil (direction of Arrow "H") from the buffer 26 (not shown) . A forward face 192 of the upwardly pivoted pick up element 50 has impacted a base surface 194 of the unfired shell 186. As a result, the shell is driven forwardly (direction of Arrow "I") from an initial shell pick up position identified by a shell outline 186a drawn in phantom lines. During forward movement of the shell 186 with the bolt assembly 24 towards the breech ring 28, the picked up shell 186 may be guided downwardly into alignment with the bore axes 42 by guide means (not shown) . When the shell 186 is so aligned, the shell base 190 is engaged, in a lower region, by the extractor 84; hence, the importance of not damaging such lower base regions when the shells are stripped from the pick up positions. Although the ejector apparatus 10 has been described as being used in association with a gas operated cannon 18 in which shell casings are ejected during bolt assembly recoil, it is to be appreciated that the ejector apparatus can be used with other types of cannon which operate on a different type of reciprocating bolt assembly principle. For example, the apparatus 10 is adapted for use with mechanically driven, as opposed to gas driven, bolt assemblies, shell casing ejection occurring during bolt assembly rear¬ ward travel and unfired shell pickup occuring on forward bolt assembly travel. Thus, although there has been described herein- above a particular arrangement of a programmed shell ejector apparatus in accordance with the invention for the purpose of illustrating the manner in which the invention may -be used to advantage, it will be appreciated that the invention is not limited thereto. Accordingly, any and all modifications, variations or equivalent arrangements which may occur to those skilled in the art, should be considered to be within the scope of the invention as defined in the appended claims.

Claims: WHAT IS CLAIMED IS: 1. In an automatic cannon having an axially reciprocating bolt assembly with extractor means operative for holding, during bolt assembly rearward travel after firing of the cannon, a fired shell casing to a forward face of the bolt assembly, and having a shell ejection opening located along the path of bolt assembly travel, programmed shell casing ejector apparatus characterized by: (a) an ejector member having a shell base engaging portion and an actuation portion; (b) means for mounting the ejector member to the bolt assembly for axial movement relative thereto; and (c) non-compliant camming means for causing, as the bolt assembly travels rearward after firing of the cannon, the ejector member to move forwardly relative to the bolt assembly at a controlled velocity which is less than rearward velocity of the bolt assembly, a fired shell casing held to said bolt assembly face by the extractor means being ejected, in response to said relative forward movement of the ejector member, outwardly through the ejection opening in a controlled manner. 2. In the automatic cannon as claimed in Claim 1, further characterized in that said camming means is *' formed having camming surfaces configured for causing the ejector member to move forwardly relative to the bolt assembly from a first position in which an ejector member shell base engaging portion is rearwardly of said bolt assembly face, to a second position in which said engaging portion projects forwardly beyond said bolt assembly face to engage and cause ejection of a fired shell casing held to the bolt assembly face by the extractor means. 3. In the automatic cannon as claimed in Claim 2, further characterized in that said camming means include at least one cam track mounted to portions of the cannon which do not reciprocate with the bolt assembly and at least one cam track follower mounted on the bolt assembly and configured to have a first portion thereof in operative engagement with the ejector member actuation portion and a second portion thereof in engagement with the cam track as the bolt assembly moves rearwardly to a shell ejection position, said cam track and follower being relatively con¬ figured for causing, as the bolt assembly moves rear¬ wardly, the ejector member to move forwardly relative to the boI % assembly from said first position in which the ejector member shell base engaging portion is rearwardly of the bolt assembly face, to said second position in which the engaging portion projects forwardly beyond the bolt assembly face to engage and cause ejection of a fired shell casing held to the bolt assembly face by the extractor means. 4. In the automatic cannon as claimed in Claim 3, further characterized in that said cam track follower is pivotally mounted to the bolt assembly and said cam track has a camming surface configured for causing, as the bolt assembly moves rearwardly with said follower second portion in engagement with said camming surface, the cam track follower to pivot in a manner causing the cam follower second portion to move the ejector member forwardly, relative to the bolt assembly, from said first to said second position, at an increasing relative velocity, whereby engagement between the ejector member shell base engagement portion and a base portion of a fired shell casing being ejected is maintained during at least initial stages of casing ejection. 5. In the automatic cannon as claimed in Claim 4, further characterized in that said cam track camming surface is further configured, relative to shape and pivotal mounting location of the cam follower, for causing substantially continuous contact between the cam track follower second portion and the camming surface during said relative forward movement of the ejector member shell base engaging portion, bouncing between the cam track follower second portion and the camming surface being thereby substantially prevented. 6.. In the automatic cannon as claimed in Claim 2, further characterized in that said camming means includes a pair of laterally spaced apart cam tracks fixed to portions of the cannon which do not reciprocate with the bolt assembly, said cam tracks having opposing camming surfaces, and further includes a pair of laterally spaced apart cam- track followers pivotally mounted to the bolt assembly, each of the cam track followers having a camming surface engaging portion and an ejector member engaging portion, said cam tracks, camming surfaces and cam track followers being located symmetrically about a vertical plane of symmetry through a barrel bore axis of the cannon. 7. In the automatic cannon as claimed in Claim 6, further characterized in that said opposing cam track camming surfaces are formed having generally parallel, laterally spaced apart forward regions, generally parallel rearward regions which are laterally spaced more closely together than are the forward regions, and inwardly converging intermediate regions which interconnect said forward and rearward regions, and in that the cam followers are configured for causing the ejector member shell base engaging portion to move forwardly relative to the bolt assembly, on rearward bolt assembly movement after firing, to cause shell casing .ejection in response to the camming surface engaging portions of the cam followers moving rearwardly and inwardly in engagement with said camming surface intermediate regions. 8. In the automatic cannon as claimed in Claim 7, further characterized in that the camming surface engaging portion of each of the cam ' followers includes a cam following arm projecting generally ourwardly away from a cam follower pivotal mounting axis and in that the ejector member engaging-portion of each of the cam followers includes an ejector member engaging arm projecting generally inwardly from said pivotal mounting axis, movement of the cam following arms rearwardly and inwardly along said cam track camming surface intermediate regions, in response to rearward movement of the bolt assembly after firing, causing pivotal movement of the cam followers about said mounting axes, thereby causing the ejector member engaging arms to pivot generally forwardly and move the ejector member forwardly relative to the bolt assembly position, from the first to the second position to cause ejection, through the ejection port, of a fired shell casing held to the bolt assembly face by said .extractor means. 9. In the automatic cannon as claimed in Claim 8, further characterized in that the cam follower pivotal mounting axes are parallel to each other and orthogonal to a barrel bore axis of the cannon. 10. In the automatic cannon as claimed in Claim 1, further characterized in that the programmed shell casing ejector apparatus includes shell pick up means mounted to a forward region of said ejector member, said shell pick up means being configured for engaging a base portion of an unfired shell located in a cannon shell loading position upon forward movement of the bolt assembly therepast and for stripping the unfired shell forwardly from said shell loading position towards a breech of the cannon. 11. In the automatic cannon as claimed in Claim 10, further characterized in that the shell pick up means includes a shell pick up element mounted to a forward region of said ejector member for pivoting between a first pivotal position in which a forward portion of said element projects upwardly substantially away from the ejector member for engaging a base of a shell located in said loading position for stripping the shell forwardly towards the hreech, and a second pivotal position in which the forward portion of the element is retracted inwardly towards the ejector member, the shell pick up means further including biasing means for urging the pick up element towards said first pivotal position for shell picking up, while enabling the pick up element to pivot to the second position in response to the bolt assembly moving rearwardly under a shell located in the loading position. 12. In the automatic cannon as claimed in Claim 11, further characterized in that said ejector member shell base engaging portion is formed having a rearwardly sloped upper forward surface region and in that the pick up element is pivotally mounted to the ejector member in a position enabling said upper forward surface region to function as a ramp to guide movement of a shell stripped forwardly from said pick up position downwardly towards a barrel bore axis as the shell is moved forwardly. 13. In the automatic cannon as claimed in Claim 1, further characterized in that a forward face of said shell — base engaging portion is formed having upper and lower rearwardly sloping surface regions forming a shell base engaging edge at the intersection thereof, said engaging edge being operative for cutting into a base of a shell casing being ejected to prevent upward movement of the casing out of engagement with the extractor means.

Inventors: STONER E
Applicants: ARES INC
Application year: 1980
Main classification: F41C15
IPC codes: F41A15