US2877690A - Counter recoil governor for a recoil type gun - Google Patents

Description

March 17, 1959 R. BARR ETAL I 23 5 COUNTER RECOIL GOVERNOR FOR A Racon. TYPE'GUN Filed Nov. 25, 1953 2; Sheets-Sheet 1 FIG. 1'

1N VEN TORS m I. III! DAVID B. MWIUGR- BY g M March 17,1959 l. R. B RR ET AL 2,877,690

COUNTER RECOIL GOVERNOR FOR A RECOIL TYPE GUN- Filed Nov; 25, 1953 I 2 Sheets-Sheet 2 O 3 m a 1 2 a Q I 3 l. a

I g a I I 7 g Y E INVENTORS man l. mu BY mun n, mwlmen COUNTER RECOIL GOVERNOR FOR A I RECOILTYPE GUN N6 (on. 89-43) inventionrelates to guns and more particularly .to a counter recoil governor for recoil type guns employing a fluidvcylinder for absorbing the recoil energy and forfreturning, the barrel to the battery position. ;-;Large,--guns;:such as those used on'warships conventionallyemploy, afluid cylinder and a piston which move relative to each other in response to barrel movement ior:absorbingrecoil energy. The piston is usually provided' With-orifices which pass fluid from one side of the piston to the other within the cylinder during the recoil and counter recoil movement. Suitable spring means is also employed to store up part of the recoil energy for effecting the counter recoil movement. Metering pins are carried by the cylinder which cooperate with the=pi tn orifices to decelerate the barrel during the last part ofthecounter'recoil stroke. In operation, when the battery position is reached the barrel should obviously have expended all its energy. If not, the excess energy islabsorbed by the barrel support cradle, producing a shockzload' which sets up vibrations frequently of sufiicient; magnitude as to damage the gun or associated equipment. If allthe energy of the moving barrel is expended; before the battery. position is reached, the breechmechanismwill not have been actuated and the gun will; not, fire. Since the amount of energy absorbed by the; orifice and metering pin system conventionally employed onlarge guns depends upon the viscosity of the fluid employed in. the braking cylinder and since temperaturehas a definite efiect on the viscosity of a fluid, consistent-results are not obtained. When the first few rounds of ammunition are fired from the gun, the fluid viscosity is greater-than when the gun has been in operation-for alonger time. 1 Since the orifices and metering'pinsuused in the present guns do not compensate for changesin fluid viscosity, difliculty is experienced in obtaining propergun operation. When the fluid is cool, the barrel frequently fails to move into the battery position after firing a round. When the fluid is warm, the barrel slams into the battery position, setting up excessively large vibrations which frequently damage the gun oriits associated sighting equipment.

. z'Ani 'objectofthe present invention is to provide agovernor:for-fiuid controlled recoil type guns, and the like, whichmontinuously compares the actual barrel velocity with the desired' barrel velocity. to control the barrel movement and automatically compensate for changes in fiuidrviscosity whereby the energy in the moving barrel will be'properly dissipated. a Another object 'of'this invention is to provide a counter recon: governor which may be used on existing recoil eras e- Still 'a'nother" object of this invention is'to provide a c usjgei' ieesn governor which is dependable in operan 1 vvhiclt may be economically" manufactured.

urther and other objects will become apparent to description esiseciauvwhen' considered in combination ll nthe' art fromareading; of the following with the accompanying drawing wherein like numerals. refer to like parts.

In the drawing:

Figure 1 is a fragmentary perspective view schematically showing the governor of this invention on a fluid controlled recoil type gun.

Figure 2 is a detail sectional side view schematically showing the governor of this invention. I Thegun, as schematically shown inFigure 1, includes a barrel 1 carried by a barrel support cradle 2 through collars 3 for limitedaxial movement relative thereto from a forwardrnost battery position as shown in the drawing to a recoil position aft of the battery" position. A barrel extension 4 formed rigid with barrel 1 serves as an abutment for engaging cradle 2 and preventing movement of the barrel forwardly of the battery position.

Axial movement of barrel 1, produced by forces developed from firing a round of ammunition, is com trolled by a fluid-filled cylinder 5 carried by cradle 2. Cylinder 5 is arranged generally parallel with barrel 1 and receives a piston 6 which is rigidly connected with barrel extension 4 through piston rod 7. Piston 6 .is provided with a plurality of orifices 8 equipped with check valves (not shown) which regulate the'flow of fluid from one side of the piston tothe other within the cylinder to control the movement of barrel 1. While the orifice arrangement in piston 6 is generally rather complicated, it is not shown in detail here since any conventional arrangement will be satisfactory for-use in conjunction with the counter recoil governor of this invention so long as the rate of energy dissipation during counter; recoil is low enough to assure return of the barrel to the battery position under all operating conditions. This requirement may be met in most cases when installing the governor on an existing gun without modifying the orifice arrangement, but by simply removing-the metering pins normally employed in 'the forward end of the fluid cylinder. A counter recoil spring 10 concentrically arranged relative to piston rod 7 within cylinder 5' adjacent the aft end 9 thereof absorbs a suflicient quantity of the recoil energy as the barrel moves rearwardly to effect the counter recoil movement back to the battery position.

Counter recoil governor 11 connects with the forward end of cylinder 5 through fluid line 12 and with the aft end of the cylinder through fluid line 13 as shown in Figure 1. A check valve 14 is interposed in line 13 between governor 11 and cylinder 5 to prevent the flow of fluid through the governor during gun recoil movement. Energy dissipation during recoil movement is effected in the normal manner by restricting the flow of fluid through piston orifices 8 and by compressing spring 10. Q 1

Barrel position and velocity information forcounter recoil governor 11 is "obtained by a rack 15 and pinion 16 arrangement wherein rack 15 is suitably carried by barrel extension 4 on the underside thereof and pinion 16 is carried by cradle 2. Pinion 16 connects with a flexibleshaft 17 through gear box 18 to rotate the shaft in response to axial movement of barrel 1. The rotational position of the shaft represents the axial position of the barrel relative to'the battery position and the rotational velocity of the shaft represents the actual velocity of the barrel. It should be appreciated that any suitable arrangement for rotating'shaft 17 may be employed without departing from the teachings of this of barrel-"1 during counterrecoil movement.

invention.

The construction of counter recoil governor 11 is shown in Figure 2 wherein the flow of fluid through a master valve 19 regulates the rate of energy dissipation An inlet port communicates with fluid line '12 and with a genoutlet port 22 providesv fluid; communication between valve chamber 21an'd fluid line 13. .Master valve 19- comprises a flow control piston 23and a guide piston 24 connecting with thev control piston through a spacer rod25 so that-fluid may flow from inlet port 20 to one let port22 through chamber 21 atarate regulated by the axialpositionofvalve19.; I I V Valve 19 is positioned within chamber 2l'byjfluid' pres- ;sure applied: thereto through ports 26 and 27 located I crally cylindrical master valve chamber ,21- which slid ably receives valve 19 for limited axial movement. An

meat shown in Figure 2. A cam 41, operatively engag. ing a suitable gear train 42 driven by shaft 43, is shaped to-represent the desired velocitycurve, for the gun bar,- I I I rel during counter recoil. Shaft -43operativley connects .with. flexible shaft 17 through a suitable coupling 44 so that-rotation-of shaft.17' is-transmittedtov shaft. 43. A

compression spring, acting between pilot valve 31 :and

1 cam 41 produces a force representing the desired velocity of the barrel. continuously-during counter recoil as dici I tatedby the shaped cam 41.- Spring45 is suitably,

I supported by a pair of telescoping members 46 and 47 at either end of the chamber; Ports 26 and 27 ,com:

The 'fiuid in pilot valve chamber 28'is fed to ports :26

and 27 in accordance with the axial position; of a pilot; valve 31'. Valve-31 c'omprisesapair of spaced control j pistons 32 and 33 which cooperate with an annular: :re I

cess 34 in communication with port 291 to allow fluid I flow into one of the ports 26'or 27 depending upon j: the axial position of the pilot valve; I ;When valve 31 is centered in chamber 28-, ports 26and 27 are. bothclosed I to fluid flow from port 29. 'When' valve 31'is' moved to the 'rightjof center asviewed in Figure 2, fluid will flow .'velocity is produced by a suitable ;fly+weight tvpeof I through 1301126 and apply pressure to. control piston,

j .23 inmaster cham'berZl, causingmaster valve 19 to:

' move 3 to. the right and reduce the fluid flow from the governor. into line 13.- This increases the backpressure.

in cylinder 5 to increase the rate of energy dissipation of: I

barrel 1 and hence: reduce the barrel velocity. :On the other hand; when valve 31 is moved to the left ofzceirter, fluid will flow through port 27' and apply pressure I to guide piston '24. causing valve 19 to move to, the left and increase the fluid flow from the governor to line 13 which reduces the rate of energy dissipation and hence decelerates the barrel less rapidly.

When port 26 is in fluid communication with port 29, port 27 is completely blocked and vice versa. Thus, it is obviously necessary to vent the portion of valve chamber 21 on the one side of valve 19 which is sealed off from port 29 since the fluid contained therein will otherwise prevent the desired movement of the valve. Therefore, vent ports 35 and 36 are employed in pilot valve chamber 28 which feed into outlet port 22 at openings 39 and as shown in Figure 2. Outer pilot valve pistons 37 and 38 are spaced from inner pilot valve pistons 32 and 33 such that only the port 26 or 27 which is sealed off from port 29 is in communication with its associated vent port 35 or 36. Thus as fluid at the inlet pressure is forced against one end of valve 19, the fluid acting against the opposite end thereof is bled ofl through the associated vent port 35 or 36 against the action of the lower outlet pressure.

From the description set forth hereinabove, it is believed apparent that by simply controlling the movement of pilot valve 31 the fluid back pressure in buffer cylinder 5 will be regulated to control the movement of barrel 1.

Control of pilot valve 31 to assure the proper rate of dissipation of energy of the gun so that barrel 1 will always reach the battery position without an excess of energy is accomplished by generating. control forces tends ing to reduce the difference between the actual barrel velocity and the desired barrel velocity to zero continuously during counter recoil and applying these forces to valve 31.

A pilot valve positioning force proportional to the de-. sired barrel velocity at any barrel position relative to the battery position is produced by a cam and spring arrange- 7g concentrically arranged relative thereto v Member '46 is slidably carried withinpilotvalvechamber 28 adjacent one end; thereof. to butt against pilot valve piston. 38. I Member 47 is provided'with a tongue 48 which slidably carried in ways 49 to permit only: axial movement of theimernberrelativeto pilot valve chamber 28. The i I outer endSO of member 47 carries a roller. 51 through pin 52. RollerSl isarranged to engage cam 41 so that I the axial position ofmember 47 relative to'member 46 'is controlledby the rotationalpositionzof the cm. In: this way compression spring 45. is causcd topproduce :a positioning force on pilot valve 31 which; represents I the desiredvelocity of the gunbarrel at 'alltimes during I counter recoil movement.

. The; positioning; force applied to pilotvalve 31whicb. I

[ s roportionalito'thedesired: barrel, velocity is opposed,

.by a positioning force applied to: the pilot valve in the opposite direction whichtis proportional to the actual barrelvelocity; The-force representing theactualbarrel governor53 such as is shownin Figure 2. j A transverse bracket 54 isrigidlyattached to a shaft SS- rotatablycar- I I riejdby support 256. Bracket St swingably carries a pair of weights 57 and 58 so that as shaft/55 is rotated, can-- trifugal; force. causes the :weights: to swing outwardly from the shaft. Projections 59 and 60 on weights 57 and 'SScngage; acollar 61 slidably carried by shaftSS and cause it to move along'the shaft as the rotational velocity increases. A compression spring 62 actsbctweencollar I 61 and axially movable flange member 63 to produce a positioning force representing the rotational velocity of shaft 55 due to the action of weights 57 and 58 when rotated. Flange member 63 is supported by a shaft 64 which is slidably received within an aperture formed in shaft 55 and by a second shaft 66 supported from within pilot valve chamber 31 through idler pistons 67 and 68. The force produced by compression spring62 is transmitted to pilot valve piston 37 through flange member 63 and shaft 66. To prevent shaft 66 and its associated idler pistons 67 and 68 from rotating when shaft 55 is rotated, flange member 63 is rotatably connected to shaft 66 through suitable bearing means 69., and idler piston 68 is provided with a key 70 adapted to slide in keyway 71 formed in valve chamber 28. I

Rotation of the fly-weight type of governor 53 topro' duce a pilot valve positioning force representing the actual barrel velocity is accomplished by operatively connecting shaft 55 to shaft 43 through a suitable gear train 72; An overrunning clutch 73 associated with shaft 43 pro vides a positive drive for governor 53 during counter recoil of barrel 1 and allows shaft 55 to slow downgrad+ ually from friction forces even though shaft 43 is stopped abruptly.

The operation of the. device is believed obvious from a reading of the foregoing description. Whenthe gun is fired, the recoil forces are absorbed in the conventional manner as the :barrel moves aft by the regulatedfluid flow through orifices 8 in piston 6 and by the compress: ng o he sa nter scoilr t in .1 Ch skvalv 14i fluid line .3 Pre n fl id 419 hmush s ua rs il governor 11 during the recoil movement. Whenallthe recoil energy is dissipated, counter recoil spring 10 urges barrel 1 forwardly towards the battery position. Duri this return or counter recoil movement, all Q! Wil Wm-FW:

em nent) portion otithefluid cylinder f' ia 'f'oi ced'through counter recoil governor 11. The rate at which the fluid is allowed to flow through the counter recoil governor is regulated by continuously comparing the actual and the desired barrel velocities. V Counter recoil movement of'barrel 1 causes rotation bfflex'ible shaft 17 and shaft 43 through therack' 15 and :pinion16 arrangement shown in Figure 1. Cam 41, driven from shaft 43, as shown in. Figure 2, is shaped tqcdmp'ress spring 45 a varying amount depending upon axi al'pos'ition of barrel l'to produce a force represeiiting'the'desired barrel-velocity. At-the same time cam 41 is operating to provide a force representing the desired barrel velocity, fly-weight governor 53 compresses a spring 62 to produce a force representing the actual barrel velocity. These two forces are applied to pilot valve 31 to control the operation of counter recoil governor 11. If the barrel is moving at a velocity different from the desired velocity, the velocity error is detected by springs 45 and 62, causing valve 31 to move so as to modify the rate of fluid flow from the forward end of cylinder 5 and thereby cause the barrel to again travel at the desired velocity. This velocity control inherently causes the proper dissipation of energy. The corrective action of the counter recoil governor is applied to the system continuously to always maintain the actual barrel velocity substantially equal to the desired barrel velocity during the return stroke irrespective of changes in the fluid viscosity. When the barrel reaches the battery position, its kinetic energy will have been completely expended so that the vibrations normally experienced with conventional buffer arrangements is eliminated.

The counter recoil governor described hereinabove may be used with equal facility for controlling recoil movement of the gun barrel in the same manner as the counter recoil movement is controlled. Obtaining control by comparing the actual barrelt velocity with the desired barrel velocity simplifies the gun design and assures uniform gun operation even though the viscosity of the fluid in the buffer cylinder changes and even though different sized rounds of ammunition are fired.

The speed control arrangement wherein the actual and desired velocities of the barrel are compared may obviously be used with equal facility to control the motion of a moving member of any kind and is not necessarily limited to use in connection with a gun.

It is to be understood that certain alterations, modifications and substitutions may 'be made to the instant disclosure without departing from the spirit and scope of the invention as defined by the appended claims.

We claim:

, 1. Counter recoil regulating means for recoil type guns having a barrel support and a barrel reciprocable with respect thereto, a fluid cylinder carried by said barrel support, a piston carried within said cylinder and fixed to said barrel for reciprocating motion therewith, regulator means connecting with said cylinder at either end thereof and providing fluid communication to both sides of said piston whereby barrel movement may be regulated by controlling the flow of fluid from said cylinder, said regulator means including a master valve controlling the flow of fluid from said cylinder, a pilot valve controlling the master valve, means sensing the actual speed of barrel movement for producing a pilot valve positioning force proportional thereto, means sensing barrel movement for producing -a pilot valve positioning force proportional to the desired velocity of the barrel, means for applying the difierence between the forces produced by the last two mentioned means to said pilot valve for controlling said master valve and regulatingthe flow of fluid from said cylinder to obtain the desired barrel counter recoil movement.

2. Counter recoil regulating means for recoil type guns having a barrel and a barrel support comprising, a fluid cylinder carried by said gun, a piston carried within said cylinderand fixed to" said pan-e1 for axial movement therewith relative to said barrel support, governor means carried by said gun for producing a forcere'presenting the actual velocity of said barrel relative tosaid barrel support a Dreamed y said gun, said cam being operatively connected to said barrel and shaped to represent the desired velocity-of said barielfl spring means compressible by said cam to produce a force representing the desired velocity of said barrel,"valve ineans regulat ing'the flow of fluid within said cylinder fromone side of said piston to the other, and valve control means operable by the forces produced by said governor means and said spring means for-actuating said valve means to effect the desired barrel movement.

3. Counter recoil regulating means for recoil type guns having a barrel and a barrel support comprising, a fluid cylinder carried by said gun, a piston carried within said cylinder for axial movement'relative thereto, saidpiston being fixed to said barrel for movement therewith relative to said barrel support, means for sensing barrel movement relative to said barrel support for producing a force proportional to the actual velocity of said barrel, means for sensing barrel movement relative to said barrel support for producing a force proportional to the desired velocity of said barrel, and valve means operable by the forces produced by said last two mentioned means for controlling the flow of fluid within said cylinder from one side of said piston to the other whereby the desired counter recoil barrel movement is obtained.

4. In a recoil type gun having a barrel support, and a barrel movable relative to the support for absorbing recoil loads, energy damping means carried by the barrel support for regulating the movement of the barrel, means connecting with said energy damping means for generating a force representing the desired barrel velocity, means connecting with said energy damping means for generating a force representing the actual barrel velocity, and means comparing the forces generated by the last two mentioned means and operatively connecting with said energy damping means for varying the damping action thereof to maintain the actual barrel velocity substantially equal to the desired barrel velocity.

5. A gun comprising a barrel support, a gun barrel carried by said support for limited recoil movement relative thereto, a piston carried by said barrel for movement therewith relative to said barrel support, a fluid cylinder carried by said barrel support and containing said piston for sliding movement therein, fluid flow control means providing fluid communication from one side of said piston to the other within said cylinder, a rack and pinion carried by said gun, by said rack being fixed to said barrel and movable therewith relative to said support to drive said pinion, a shaft operatively connecting with said pinion for rotational movement therewith, a pair of spring means carried by said fluid flow control means, cam means driven by said shaft and engaging one of said pair of spring means for deflecting the latter and producing a force representing the desired velocity of said barrel, governor means connected to said shaft and engaging the other of said pair of spring means to deflect said other spring means for producing a force representing the actual velocity of said barrel, and means actuable by both said spring means for regulating said fluid flow control means and maintaining the actual barrel velocity nearly equal to the desired barrel velocity.

6. A governor for controlling the velocity of a movable member comprising, a shaft, means carried by said movable member and connecting with said shaft to produce rotation thereof at a rate proportional to the actual velocity of said movable member, a pair of opposed spring means, variable control means connecting with said movable member for regulating the movement thereof in accordance with the combined force exerted by said spring means, cam means driven by said shaft at a rate proportional to the actual velocity of said movable deflected by the movement of said weight to produce a force representing the actual velocitypof said movable member whereby to vary said control means in cooperation with the other of said pair of spring means to maintain the actual velocity of said movable member nearly equal to .the desired velocity.

Retemaces Cited in the fileofi thisflipatent it UNITEDSTATES PATENTS Reid May 17, 1932 Simpson Dec. 5,1944 French Apr. 24, 1945 Lucht Feb. 26, 1946 Cantley et a1. Oct. 15, 1946 Drake Dec. 2, 1947 Mergen et a1. Oct. 18,1955

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