US2498033A - Gun control mechanism - Google Patents

Description

Feb. 2l, 95@ H. ERNST ETAL 2,498,033

GUN CONTROL MECHANISM Filed No'v. 22, 1937 6 Sheets-Sheet l Jiffy 7 Feb., 2E, 1950 H. ERNST ET AL 2,498,033

GUN CONTROL MECHANISM Filed Nov. 22 1937 6 Sheets-Sheei'l 2 i? Eg? if Feb 2L i195@ H. ERNST ETAL GUN CONTROL MECHANISM 6 Sheets-Sheet 3 Filed NOV. 22, 1957 NNN Feb 2l, E95@ H. ERNST ETAL 2,498,033

GUN CONTROL MECHANISM Filed Nov. 22, 1937 6 Sheets-Sheet 4 Feb. 2l, E950 H. ERNST ETAL. 2,498,033

GUN CONTROL MECHANISM Filed Nov. 22, 1937 6 Sheets-Sheet 5 Feb. 21, 1950 H. ERNST ETAL 2,493,033

GUN CONTROL MECHANISM Filed Nov. 22, 1937 6 Sheets-Sheet 6 Parenteel rele. 21.1950 '2,498,033

UNITED STATES PATENT OFFICE GUN CONTROL MECHANISM Hans Ernst and Bernard Sassen, Cincinnati, Ohio, assignors, by mesne assignments, tothe United' States of America as represented by the Secre-` tary oi the Navy Application November 22, 1937, Serial No. 175,830

8 Claims. (Cl. 89-41) 1 2 This invention relates toV motion transmitting Figure 7 isa section on the line 'l-'l of Figor signaling systems and more particularly to ure 1. the type. wherein a follower is caused to move Figure 8 is a section on the line 8--8 of Figin synchronism with a transmitter or director. ure 7.

One of the objects of this'invention is to pro- 5 Figure 9 is a'se'ction through a transmitter vide an improved system which is highly sensitiveunit.

to any movement of the transmitter; which is Figure 10 is a section on the. line Ill-I0 `oli positive in operation; and which is capablev orv Figure 9. p developing the necessary torque for effecting Figure 11 is a, section on the line ll-ll of movement of a receiver and also maintaining 10 Figure 10. the same in synchronous relation with the trans.- Figure 12. is a section on the line I 2-K-l2 of mitter. Figurey 6.

Another object of this invention is toA develop Figure, 13 is a section on the line |3--l3' of a system of the character mentioned which al- Figure 6.

though sensitive to a high degree, may be of 15 Figure 14 is a section von the line Isl- I4 of rugged construction, thereby eliminating delicate Figure 6.

parts susceptive of easy breakage, or sensitive to Figure 15 is a section on the line I5-I5 of shocks causing maladjustment. thereof. Figure 6.

A further object of the invention is to provide Figure 16 is a section on the line lB-IG of a system as aforesaid in which hydraulic means 20 Figure 6. may be utilized as the motion conveying or sig- Figure 1'7 is a diagram of' the hydraulic renaling medium, sistances.

An additional object of this invention is to Figure 18 is a diagrammatic View Showing the provide a system of the character mentioned relation between the change of resistance in the which may be compounded in such a manner 25 transmitter elements relative to the change of that movement; in a plurality of planes may be resistance in the receiver elements.

placed under the control of a single element, This invention in its broad aspects, contemthereby providing a system whichA is; suitable for plates a signaling system forkthe transmission nre control purposes of military forces and espeof motion impulse signals from a transmitter to cially adapted for control of anti-aircraft defense 3f) a receiver in a definite and positive manner, and so that one will always be in synchronism with weapons.

Other objects and advantages of. the present the other, whether at rest or in motion. In the invention should be readily apparentA by referattainmentof absolute synchronisma constantly vence to the following specification, considered in acting force. must be ever present so that even conjunction with the accompanying drawings u after a. signal has been transmitted, the interillustrative of one embodiment, thereof, but it will connected parts will be held and maintained in be understood that any modifications may be their new positions thereby preventing Vinadmade in the specific structural detailswithin the vertent or accidental movement of the` receiver scope of the appended claims without departing out of synchronism with its transmitter or difrom or exceeding the spirit of the invention. ,N rector. More speciiically, this invention contem` Referring to the drawings in which like4 referplates a signaling system in which yan hydraulic ence numerals indicate like or similar parts: medium isutilized for transmittingl signals such Figure 1 is an elevation showing the applicaas motion impulses, and which is so contrived tion of the invention toanti-aircraft gun control. as. to provide aiirst group of properly related Figure 2 is a sectional View onthe line 2-2 of pressural control elements in thev transmitter Figure 1. which act through individual hydraulic lanes to Figure 3 is a sectional view on the line 3-3 of alter or unbalance the respective kpressures on Figure 1. v an equal. group 0f receiver actuators arranged Figure 4 is a view similar to Figure 2L showing to be effective as a couple to cause movement of a modified form of gearing between the transan ultimate receiver element, which movement -m-itter and receiver. will continue until the actuators themselves by Figurev 5 is a view similar to-Figure 3.showing theirown movementv cause reequalization of the a modied form of gearing. pressures acting upon them, and therebyV equil- .the receivery motive power units.

Figure 6 is a longitudinal view through one of librium between the parts.. which not only stops the receiver elementbut holdslit in a given position. Accurate positioning is obtained because each increment of movement of the director causes a denite pressure differential on the actuators which will not be eliminated until the receiver actuators have moved through that same increment.

Having effected a new position, the fluid pressure still acts but in an equalized manner so that even if the receiver actuators are inadvertently 01 accidentally disturbed, the fluid pressure will again bring them into synchronized relation with the respective control elements. Such a system is thus admirably adapted forcontrolling, for instance, the azimuth or elevation of a gun from a remote re control station and more particularly for` controlling the position of anti-aircraft defense weapons. On account of the rapid movement of aircraft, it is extremely difficult to follow their movements with the ordinary gun sights because alignment ofthe sights with the target means movement of the gun, which is so-unwleld 1y as to prevent easy and fast manual movement thereof. It is therefore desirable to use independent, easy and quickly movable sighting apparatus for this purpose. It is obvious that the movements of this apparatus must be immediately transmitted to the gun so that it will always be in a position to fire as soon as the target is properly located. In such a combination the sighting apparatus can be considered as the transmitter; and the gun as a receiver thus presenting an ideal condition for the application of this invention and it will therefore be described in connection with an anti-aircraft defense Weapon for control thereof. l

lThe relative position of Such a gun and its control mechanism may be the same as that shown in Figure 1 inwhich the reference numeral I indicates generally the gun, While the reference numeral II indicates in a general manner the control for the gun. Since aircraft in general are capable of three ,directional movement as distinguished from the two directional movement of ordinary land or naval forces, it is necessary that thev weapons used to combat aerial forces have a greater range of adjustment than the ordinary land and naval weapons; and for this reason, the gun barrel II is carried or mounted on a support I2 which has limited angular movement about a pivot I3 and in the plane of the upper surface I4 of a sub-support I5. This subsupport is mounted for movement about a pivot i I5 for elevational adjustment of the gun, the pivot being carried by a column or standard I1 which itself is angularly adjustable in a horizontal plane about a pivot IB, the Weight of the standard being transmitted through anti-friction bearings to a base member 20. It will thus be seen that the gun may be adjusted in a horizontal plane about the pivot I8; in a vertical plane about the pivot I6, and in an inclined plane about the pivot I3.v

The sighting apparatus must be capable of corresponding movement in these various planes in order to properly control the gun by merely sighting the target, and for'this reason the director or sighting arm 2I, carrying sights 22, at opposite ends thereof, is mounted for movement about a pivot 23, carried by a sub-support 24, mounted for angular movement in a vertial plane about the pivot 25. The pivot 25 is carried by a vertical standard 26 which is mounted for rotation about a pivot 21, its weight being transmitted to the base 28 through anti-friction bearings 29. The director arm 2l may be moved through means of the hand grasp 30, secured to one end thereof,

vinch as shown in 5S inFigure 11.

4 by the gunner or other operator, in a vertical plane, or for limited movement in any inclined plane about the pivot 23, 01 for complete movement through a circle about the pivot 21. Since the movement about the pivot 21 is effected by a separate hand grasp 3I integral with the member 26, the movement about "the pivot 23v is provided so that small adjusting movements may be made more quickly than if dependence was placed upon the control 3 I.

Mechanism has been provided whereby any movement of the sighting apparatus will be lmmediately communicated to the corresponding movable elements of the gun so that the axis of the gun will always be in synchronism with the axis passing through the sights 22. The sighting apparatus therefore constitutes a form of transmitter which is utilized to signal the movements to be made in the gun, the system contemplated by this invention effecting the gun movements automatically, and simultaneously with the movement of the sighting apparatus.

A separate transmitter, such as shown at 32 in Figure 9, is operatively connected vwith each movable element so that the movement in the respective planes is transmitted by individual transmitters. Similarly, each of the movable parts of the gun support is provided with an individual receiver which is Aof the same form as the transmitter 32 shown in Figure 9, and this receiver is coupled for control of an hydraulic motive power unit for translating the signal received into power movement of the gun. It should thus be obvious that the `three possible planes of movement of the sighting apparatus have three separate transmitters which are connected to individual receivers in the gun, thereby constituting in effect three separate and distinct communication or signaling systems. Since all of the systems are the same, only one will be described hereinybut it is to be remembered that even although they function as separate entities they still may be provided with uid pressure from a common source.

As shown in Figures 9, 10 and 11, the transmitter comprises a housing 33 containing a cylinder block 34, in which is formed a plurality of cylinders 35, 36, 31 and 3-8. Piston members 39, 40, 4I `and 42 are mounted in the respective cylinders 35, 36, 31 and 38 for movement toward and from a common center member 43. Each piston has an anti-friction roller 44 journaled in the outer end thereof for cooperation with the inner contoured surface 45 of the manually rotatable member v46. The cylinder block 34, as more particularly shown in Figure 11, is interdrilled to provide a passage 41, to which the pressure channel 48 is connected when the device is used as a transmitter. When the device is used as a receiver a reservoir return line is connected to this passage. The passage 41 is connected by four axially extending holes49, 50, 5l and 52 to separate angularly shaped passages 53, 54, 55 and 56. These passages terminate in ports intersecting the respective cylinders, there being two ports on opposite sides of each cylinder so that the pressure serves to balance the'pistons in the cylinders and prevent binding thereof. Each piston has a pair of grooves 51 formed on opposite sides thereof. Also, the portions of the periphery of the piston between the boundaries of the grooves 51 are reduced in diameter by afew thousandths of an A diametrical hole 59 in the piston interconnects the'grooves 51 with an axial yhole 50 drilled in-oneend of each piston, these yaxial holes terminating at the space 6l existing at the inner end of each cylinder. The spaces 6l communicate with separate passages 62, 63, 64 and 65` formed in the center portion of the cylinder block and each in turn is connected with a separate pipe extending to the receiver'. When the device shown in Figures and l1, is utilized as a transmitter, uid .pressure may be supplied, as by the channel 48, to the cylinder ports, through which it then passes to and through the narrow spaces 66, 61, 68 and 69, which constitute hydraulic resistances, to the intersecting passages 59 and '63, and from there through the spaces 6| to the respective channels 62, B3, 64 and 65. These .hydraulic resistances .cause a drop in .pressure between the lincoming fluid in channel v48 and the outgoing iluid in channels 62, `63, 64 and `65. Also, the hydraulic resistances will cause a. dierent drop in 'pressure for each piston, depending upon the axial .position thereof in its cylinder, it -being apparent that when the piston 39, for instance, is at the limit of its outward stroke, the resistance will be at a maximum; while when the piston, such -as 4i, is at the end of its inward stroke the resistance will be at a predetermined shaped sur-faces lll, each of which has the same contour and which are so formed that upon movementof the member l446 through an arc lindicated by the reference numeral 1I, the piston will -bev moved inward through a complete stroke causing the hydraulic resistance to vary at a substantially uniform rate from maximum to minimum, 'or from minimum to maximum "depending upon the direction of rotation yof the cam 46. Upon unidirectional movement of `.the lmember 46, one half of the surface 7U may be considered as a piston advancing portion and ythe other-half as a piston retracting portion.

When `the device shownin Figures 10 .and 11 is utilized .fas 4a receiver, the direction of flow .through it will be reversed, the uid entering through channels 62,63, 64 `and 65 to act on the lends of the pistons and cause clockwise or -counter-clockwise rotation of the member 46 and discharging through the hydraulic resistances in the various pistons `to a return channel, which would be lsubstituted for `the channel .48.

It -will thus beenseen that the system in its elementary form comprises a source of fluid pres- -sure which isvconnected to a plurality of parallel resistances which are simultaneously variable, .as

:by manual rotation of the member 46, in prede- Jtermined relation to one another, and a serially Aarranged equal number of resistances, which are automatically variable in the same phase rela- 4tion so that denite pressures are created Ibetween the respective pairs of serial resistances,

:such yasin the channels 62, 63, 64 and 65and that the pressures in these channels may be 'varied by changing the resistance at either rside thereof.

In order to more clearly understand this relationship, a simple diagram has been shown in Figure 17 in which the pressure supply line .is represented by the numeral 12; Vthe hydraulic resistances associated with pistons 39, 4U, 4|' and 42 by the respective resistance coils 13, 14', 15 and 16 while the corresponding resistances in the receiver member are dagrammatically llustrated by the coils Tl, 18, 19 and 80, the respective pairs of resistances being interconnected by channels 62', 63', 64' and 65 corresponding to channels 62, 63, 64 and 65 in Figure 10. The fluid escaping from the resistances 11 to 80 inclusive may be connected in a common return line 8| and returned to a common reservoir. Although the channel l2 has been indicated as a pressure channel and the channel 8| as a return line, the functions of these could be reversed without changing the eiect or operation of this device.

Although four lines have been shown in Figure 17,` a minimum .of three parallel lines could bev used; but since `such an arrangement would not produce uniform turning torque throughout the 3 60 degrees. of movement of the device, it .is preferable to use ya larger number although. the actual number used does not depart fr om the principles of this invention.

By using tour channels, it is. possible toarrange the pistons in Opposing pairs, or in other words, in couples, so that while one pair is passing a dead center, the -other pair is active and capable `of 'causing reverse rotation of vthe receiver.

It is a Well-known hydraulic principlethat the pressure P in a channel is a `function of the quantity-Q flowing through the channel, yand the re-f sistance R in the .remainder of the channel be# tween the point-where the pressure is taken and the outlet; and this relationship may be expressed as n 'Figure 1'7 a portion of the various parallel branch lines indicated as 53', 54", 55 and 56' correspond respectively to channels'53, 54', 55 and =56 'in Figure` 10. The pressure in each of these lines will be the same as the pressure inthe -mainsu-pply Aline 'I2 and therefore in'accordance with the preceding equation, a vseparate equation may be written forr each parallel 'branch line. In these -equatio'nsQ Q2, Q3, and' 'Q4 represents the quantity o lowintherespect'ive branch lines.

Alsoif tP1l=2,`1 3, andPrepresent the pressure in lthe respective channels 62" 63', 64' and 65.' `we may-writethe following equations: i

.Dividing Equations i5., 6,.'7 and 8 by Equations f1, 2, f3 and .4 respectively, we have in simplified form:

ananas It will therefore be apparent that the respective pressures P1, P2, P3, P4 are each equal to one-half of the pressureA in the main line 12. In other words if the resistance to ow in is equal to the resistance to flow out of a given channel the pressure intermediate the resistances is always equalv to one-half of the supply pressure. It should be remembered, however, that this does not means that because resistance 13 is equal vto resistance 11, for instance, that the resistance 13 must be equal to the resistance 14 or resistance 15, or the resistance 16. Each one of these four resistances may have different values but so long` as the remaining serial resistance is equal to the first resistance, the intermediate pressure will be one-half of the supply pressure. It is thus possible to have the piston 39 at the end of its outward stroke, and the piston 4| at the end of its inward stroke, one presenting a maximum of resistance and the other a minimum resistance, and ystill have the pressure at 62 and 64 in Figure 10 equal to one another. Similarly, the pressure at 63 and 65 may be equal to one another, and since all four pressures are equal, no movement will result in the rotatable member 46.

The change in resistance caused by any piston may be plotted against the length of piston stroke as shown by the graph 62 in Figure 18 in which the distan-ce X represents the length of piston stroke and the distance Y represents the change in resistance from any predetermined minimum to any predetermined maximum. The orifices or ports and the surfaces 45 are so shaped that this changein resistance is substantially uniform throughout the length of piston stroke. Also, since the length of piston stroke corresponds to the movement of the member 46 through the arc 1| the length of piston stroke might also be .considered the length of .angular movement of the member 46 through the arc 1|. Therefore, a reference line 83 has been drawn in Figure 18 and the graphs 84, 85 and 86 positioned relative to this reference line in accordance with the phase relationship of pistons 4|, 40 and 42 respectively relative to the piston 39. In other words the hydraulic resistance of piston 39 is at a maximum, as indicated by the point 81 in graph 82, the hydraulic resistance of piston 4| is at a minimum indicated by the point 88 in graph 84, the resistance of piston 40 is substantially intermediate the minimum and maximum resistance possible as indicated by the point 89 in graph 85; and similarly the resistance of the piston 42 is the same as piston 40 as indicated by the point 90 in graph 86. If the reference line 83` is considered to be the member 46, it will be seen that if this line is moved in the receiver member.

8 direction of the arrow 9| corresponding to clock'-r wise movement of the member 46 such as to the position indicated by the dash and dot line 92 that the resistance of piston 39 will decrease from the point 61y to the point 93; the resistance-,of piston 4| will increase to the point 94; the re-` sistance of piston 40 will decrease to the point 95, and the resistance of piston 41 will increase to the point 96. Conversely, if the line 83 is moved in the direction of arrow 91, corresponding to the counter-clockwise direction of member 46, the hydraulic resistance of the various pistons will change in accordance with the graphs 98, 99, |08 and |0|. A second set of graphs |02, |03, |04 and |05 have been drawn to represent the corresponding hydraulic resistance in the Since the transmitter `and receiver should always be in the same relative position, these graphs will be in the same phase relationship to the reference line |06 as the preceding set of graphs whereby the resistance as indicated by the points |01, |08, |09 and ||0 will be equal to the preceding resistances and should change in the same relationship. The respective pairs of resistances have been connected by channels 62', 63', 64' and 65 in accordance with Figure 17. It will now be seen that when the resistance in to line 62' is equal to the resistance out of it, that the pressure in this line will be equal to one-half the main pressure, and since the same is true with channel 63 it will be seen that the pressure on opposite sides of the intermediatevpiston will be the same and no movement will result. Also,

. the pressure on opposite sides of the piston ||2 intermediate lines 64' and 65' will be the same and no movement will result.

If now the member 46 is rotated in a clockwise direction indicated by the arrow 9|, there will be a momentary unbalancing of the pressure in the various channels due to the fact that the resistance in in all of these channels is now different from the resistance ou of them. In other words, the pressure P1 in channel 62 has decreased which will be evident from equation 9,

because the resistance 11 will now be less and therefore P1 will be a smaller fraction of the pressure P than it was formerly. Similarly the pressure at P2 will be increased due to the increase in the value of the resistance 18. Since vthe pressure in channel 63 is now greater than the pressure in channel 62', there will be an unbalancing of the forces acting on the piston 'and in such a direction as to cause clockwise movement. Also, the pressure at l?3 in line 64' will be less than the pressure in channel 65 which again will act on the intermediate piston |12 to cause clock-wise movement. This clockwise movement is equivalent to movement ofthe reference line |06 to its dash and dot position indicated by itsreference numeral |06'. When this position is reached, it will be seen that the resistances will now be equal to the incoming resistances and the opposing pressures and the pistons and I2 will again equalize, restraining any further movement and simultaneously maintaining the parts in a fixed position.

vThe pressure on opposite sides of the pistons and |12 diagrammatically represent the opposing pressures on the pair of pistons 39, 4| and on the pair of pistons 42 and 40. It should now be clear that when the transmitter member 46 is rotated either clockwise or counterclockwise, that differential pressures will now be set up in channels 62, 63, 64 and 65 which will cause the '9 pistons in the receiver member to assume the same position as those in the transmitter, or in other words be in `synchronous relation therewith.

One form of construction `by which the transmitter is interconnected with the receiver is shown in Figures 2 and 3, the transmitter being shown in Figure 3 and the receiver or gun being shown in Figure 2. I-n Figure 3 the hydraulic transmitter H3` is fixed with the column and provided with a bevel gear H4 on one end of a shaft |I5 which is directly connected to the cam member 46. A large bevel gear ||6 which is in the ratio of 6 to 1 to the bevel gear ||4 meshes therewith whereby one rotation of the gear ||6 will eifect six rotations of the cam 4G. A second bevel gear I1 is integral with gear ||6 and both are mounted vfor free rotation on the shaft |I8 carried by the column H. The gear II1 meshes with the bevel gear 9 keyed to the end of pivot pin 23 which is mounted for free rotation in the support 24 but is keyed with the support 2| which carries the sights 2'2.

The hydraulic transmitter ||3 is connected by four individual channels |28, |2|, |22 and |23 to the hydraulic receiver member |24 which, as shown in Figure 6, is mounted in one end of a housing |25. The receiver member controls a motive power unit indicated generally by the reference numeral |26 and which is coupled to the receiver in the manner of a servomotor. The output of this motive power unit is transmitted to shaft |21 having a worm gear |28 secured to the end thereof in mesh with a worm wheel |29 mounted for free rotation on the shaft |39. A bevel gear |3| is formed integral with the worm wheel and meshes with a similar bevel gear |32 which is keyed to one end of shaft |33, this shaft being mounted for free rotation on the subsupport I5 but keyed at its upper end to the gun support I I. It should now be evident that when the sight support 2| is rotated in the plane of the upper surface of the sub-support 24 regardless of the angle of this plane, that the hydraulic transmitter will be rotated through the intermediate gearing to a definite position thereby disturbing the existing pressuresin channels |20 to |23 inclusive which will cause a corresponding movement from the receiver |24 until those pressures have been equalized again, and when this equalization occurs the receiver will be in the same relative position as the transmitter. This rotation of the receiver will cause a prede.- termined movement o-f the servomotor |26 and thereby rotation of the gun support to a. position parallel to the position of the sighting vsup- The sub-support 24 has a bevel gear |34 secured thereto which meshes in six to one ratio with a bevel gear |35 secured to the end of a shaft. |36 of a second hydraulic transmitter |31. This transmitter is connected by lines |38, |39, |40 and |4| to a receiver |42 which operates in turn a motive power unit |43 connected through worm |44 and worm wheel |45 to the sub-support l5.

Y The motive power unit |26 is coupled to the receiver in a ratio of one to six so that one rotation of the receiver |24 will effect six revolutions of the shaft |21. Also the ratio of the worm |28 to the worm wheel |29 is 36 to 1 so that it will .take 36 revolutions of the worm to effect one rotation of the worm wheel. These two trains thus make -itpossible for any movement of the Agu-n sights about the pivot 23 or about the pivot II'8 to 4be vimmediately transmitted to the gun support vI I and correspondingly position it about the pivots 3 and |39 parallel to the axis of the sights carried by the support 2|. The construction' shown in Figures 2 and 3 requires a flexible hydraulic connection between the transmitter and receiver due to the fact that the transmitters are carried by the support Ill which is also rotatableabout the ,pivot I8 while the receiving elements are carried by the support I| which is rotatable about the pivot 21.

The .details 4of this flexible connection are shown in Figures 7 and 8 and comprise a tapered plug .|46 carried by lthe base 20 rotatably tting in a tapered bore formed in the housing |41 which is carried by the standard I B- and rotatable therewith. This plug has four annular grooves |29', |2I., |22' and |23 to which the channels |120 to .|23 inclusive are connected, and a second group of four annular grooves |38', |39', |48' and I 4| to which the channels I 38 to |4| inclusive are connected. Each one of these connections may be made as shown in Figure 8, the respective pipes being connected by a nipple |48 threaded in a bore .|49 formed in the member |41. These connections will be equally spaced about the outside periphery of the member |41 as .more particularly shown in Figure 1. Each annular groove is connected by a radial hole |50 to a longitudinally extending hole such .as |5|. These longitudinal holes terminate at the bottom of the member |46 into which the respective continuations of the various channels are threaded as more particularly shown at I 5?v in Figure 8. It will now be seen' that the vertical standard |10 may be rotated relative to the base member 2|! without disturbing the hydraulicv connection in these variouschannels. `The member |46 has an additional annular groove |53 to which uid pressure is supplied from a pump |54 driven by a suitable prime mover, such as a motor |55 which may be either an electric motor or an internal combustion engine if the device is used in the field remote from a source of electrical energy. The annular groove |53 is connected by the pipe 48 to the passage 41 in the transmitter as shown in Figure 11 to supply the fluid pressure thereto.

1 Since the flexible hydraulic connection increases the possible leakage from the system, it is preferable to use the arrangement shown in Figures 4 and 5 which eliminatesthe use of this connection, Inv Figure 5 thetransmitter ||3 for the rotary movementv of support 24 is carried by a bracket |56 which is integral with the base 20. The transmitter 31 is connected by a pair of spur gears l|51 and |58 'in va one to one ratio to a vertical shaftl59, this shaft being connected by bevel gearsA |60 in a one to one ratioto the horizontal shaft |6|. This shaft has integrally secured thereto a bevel pinion |62 meshing with bevel gear |63 in a six to one ratio whereby one rotation of gear |63 will effect six revolutions in the gear |62. The gear |63 is keyed to one end of the pinion 23 which is xed at the, upper end of the support 2|.

The transmitter H3 is connected by a spur gear train comprising gears |64, |65 and |66 in a one to one ratio to shaft |61. This shaft carries on its upper end ak bevel pinion |68 meshing with the bevel gear |69 xed to the support 24.

The transmitter 3 is vconnected by the hydraulic cable'fIThaving fourl individual lines inclosed therein-'to the receiver |24' in the same manner asbefor'e, thefre'ceiver in turn controls "put shaft |21 of the motor.

11 the movement of the servomotor |26 in the same manner as before. The output shaft |21 of this servomotor is connected, however, by spur gear I1I to gear |12 in a three to one ratio the gear |12 having integral therewith a pinion |13 meshing with a gear |14 in a two to one ratio, the gear |14 being carried by the vertical shaft |15. By means of this gearing, one rotation of the shaft |21 will effect one-sixth of a revolution in the shaft |15. This shaft is connected by worm and worm wheel connection |16 to the support I5, the worm and worm wheel having a reduction ratio of one to six. The transmitter |31 is connected by the cable |16' to the receiver I42-which ,controls the operation of the servomotor |43 .as in the construction shown in Figure 2, but the vservomotor is connected bya spur gear |11 to a gear |18 secured to the end of shaft |19 in a one to six ratio whereby one rotation of gear I 11 will effect one-sixth of a revolution in the shaft |19. This shaft is connected at the upper end by bevel gearing |80 in a one to one ratio to shaft `I 8 I This shaft has fixed thereto a spiral gear |82 meshing with aV spiral gear |83 in a one to six ratio, the latter gear being keyed to the end of the shaft I3 which is fixed with the gun support I I. An additional transmitter and receiver have been provided for the rotary movement of the vertical support II when rotated by means of the handle 3|. This handle has a spring pressed grip |84 pivotally mounted thereon for friction- `ally engaging a flange |85 fixed with the support 28 for holding the standard I'I in any adjusted position. The lower end of the support I I .is therefore provided with a large spur gear |86 xed for rotation therewith and meshing with .the pinion gear |81 fixed to the end of the shaft .|88 of the hydraulic transmitter |89. The ratio of this gearing is six to one whereby one rotation of the part II will effect six revolutions of the transmitter |89. This transmitter is connected by-the cable |90 to the hydraulic receiver `I9I which has the servomotor as in the previous constructions, the servomotor being connected to a worm |92 meshing with a worm wheel |93 in a 36 to one ratio, the worm wheel being carried by the lower end of the gun support I0.

The motive power unit includes an hydraulic motor more particularly shown in Figures 6 and with a port 206 and in order to obtain maximum guidance and minimum length of piston the opposite end of the piston from the roller is valso provided with a skirt 201 having longi- 'spaced planes.

ures 6 and I5, each port 206 is connected by a' radial passage 2|4 to a port 2|5. The shaft |21 has a pair of longitudinal passages 2| 6 and 2|1 formed therein which terminate in radial bores 2I8 and 2I9 which, as shown in Figure 6, lie in For instance, as shown in Figure l5, the passage 2 I 1 terminates in three radial bores 2| 9, 220 and 22| lying in one plane and the passage 2I6 terminates in three radial pas-J sages 2 I8, 222 and223 lying in a different plane. It will also be observed from Figure 15 that these six radial passages are equally angularly positioned about the center of the shaft |21, even although they lie in different planes. Each radial passage, however, terminates in an arcuate slot as shown at 224 in Figure 6 whereby all of these radial passages are adapted to cooperate with all of the motor ports 2|5 in proper succession. For instance, if the channel 2I6 is connected to a source of pressure, the pressure Will flow through radial passage 2I8 to piston I 99 which, it will be noted, acts on the lobe 2|| to cause ton. 'I'he upper end of each cylinder is provided u tudinal slots 208 formed therein, one of the slots being opposite the port 206 to maintain communication between the port and the cylinder in all axial positions of the piston and the other lslot receiving a pin 209 to prevent rotation of .the piston in the cylinder and thereby maintaining the roller 200 in its proper plane relative to the control cam 2I0. This cam has three lobes ,2| I, 2 |.2 and 2|3. These lobes are equally spaced and so arranged that itis acted upon successivelybythe pistons to cause rotation ,of the out` As shown in Figcounterclockwise rotation of the shaft 2|1 due to the fact that the point of contact 225 acts in offset relation to the center 226 of the shaft `I21. When the channel 2 6 is under pressure the channel 2 I1 is connected to exhaust and this permits the fluid acting on piston in cylinder |91 to exhaust and permit outward movement of the piston. As this rotation continues slightly beyond the position shown in Figures 13 and 16, the radial pressure channel 223 will be connected to supply pressure to cylinder |96 thereby causing inward movement of the contained piston and the radial exhaust lpassage 220 will be connected to cylinder |98 permitting the same to move outward. This sequence will continue, thereby causing continuous rotation of shaft 21 so long as pressure is supplied to channel 2 I 6 and channel 2 I1 is connected to exhaust. If the connections are reversed to these two channels so that channel 2I1 is a pressure channel and 2I6 an exhaust channel, the direction of rotation of shaft |21 will be reversed. Further, if all flow is cut oil. from these two channels the motor will stop.

The flow to these two channels is controlled by a Valve mechanism more particularly shown in Figures 6 and l2. As shown in Figure 6, the channel 2|6 is connected by a'radial port 221 to an annular groove 228 formed in the valve hous` ing 229 which is mounted for free rotation about the shaft |21. The channel 2I1 is connected by a radial port 230 to an annular groove 23| formed in the valve housing. The annular groove 228 is connected by the passage 232 to the annular groove 233 formed in the valve sleeve 234, this groove having radially extending passages 235 communicating with the interior of the valve sleeve. The annular groove 23|' is connected by the passage 236 to the annular groove 231 formed in the valve sleeve and having radial ports 238 formed in the bottom thereof communicating with the interior of the sleeve. A valve plunger 239 is reciprocably mounted in the sleeve and has a spool 240 of sufficient width to close the pressure port 24| when in a central position, and a pair of end spools 242 and 243 which normally close the exhaust ports 244 and 245. Fluid pressure is. delivered to the device through channel 246 which, as shown in Figure 16, communicates by radial passage 241 tothe annular groove 248 formed inthe sleeve 249. The sleeve 249 has a'plurality of radialholes 250 formed in the bottom of groove 248l communirating with an annular groove 25| formed-in the periphery of shaft |21. A radial bore 252 in the bottom of this groove communicates 'with the longitudinal passages 253 formed in the shaft and terminating, as shown in Figure 12, in a similar radial passage 253 through which the iiuid is supplied to the annular groove 254 formed in the Valve housing 229 and connected with port 245. The two exhaust ports 244 'and '245 are connected by passages 255 and 25e to thev remaining annular groove 251 formed in the valve body which, in turn, is connected by radial pas- 'sage 258 to the longitudinal bore 259. This bore communicates as shown in Figure 16, with a similar annular groove 260 to which the exhaust pipe 26| is connected. It will now be seen that fluid Apressure is supplied to the p-ressure port 24| and thisJ port is selectively connected to either passage 2HE or 2|1 by the spool 24% carried by the valve plunger v239. y

This valve plunger has a slot 282 formed in the end thereof for receiving a ball-ended bell crank 263 pivotally mounted at 284 in the valve housing I229. The other arm 265 of this bell crank has a bifurcated slot 266 in which ts a f pin 281 carried by, as shown in Figure 14, a rotatable plate 268 fixed as shown in Figure 6, to the cam plate 45. It will now be apparent that as the cam plate 4K5 of the receiver member is rotated, it will act through the plate 258 and pins 269 to oscillate the bell crank 263 vand move Athe valve plunger ina p-redetermineddirection to connect the pressure port 24| to either passage 2|'6 or 2|1 and thereby cause actuation of the motor kwhich in turn will cause clockwiseor counter-clockwise rotation of the output shaft '239 so as to centralize the spool 240 with'respect f 4to the pressure port 2M. As previously mentioned,` the motor operates in a six to one ratio with respect'to the receiver and therefore the feed back mechanism must be of such construction as to permit six times the angular movement of receiver member Se in the shaft |21 before terminating the movement thereof. To this end the shaft |21 is provided with a pinion gear 210 on the end thereof meshing with the spur gear 21| which is journaled on a shaft 212 carried by the valve housing 229 for movement therewith. The gear 21| meshes with. an internal gear 213 which, as shown in Figure 6, is fixed with the outside housing of the motive power unit. This gearing 'is in such a ratio that as the shaft 2|1 rotates, it will cause the gear 21| to travel with respect to the fixed internal gear N3 and cause rotation of the valve housing 229 about the axis of shaft |21 .and in a direction to follow up the movement of the valve plunger 239 caused by rotation of plate 258. f

There has thus `been provided an improved mechanism for transmitting motion from a moyable object, such as the sighting element of a vfire control system for anti-aircraft defense weapons, to the weapon itself, including pairs of interconnected hydraulic synchronous devices whereby movement of one causes a synchronized movement of the other, together with a power arnplifying means consisting of a servo-motor consito trolled by' the 1 receiver 'synchronous device, whereby the large torque necessary to move the gun will be produced by the yservo-motor and only a-small torque willbe necessary to transmit the motion from the transmitter to the receiver.

What is claimed is:

l. In a signaling system, the combination of arotatable transmitter, a remotely located rotatable receiver, a plurality of Aopposed pairs of fluid operable devices connected in couple formation to the receiver, a source of pressure fluid, means conducting the uid for continuous flow to and from said devices, resistance means in the iow from said devices for vcontrolling the individual pressures thereon, additional resistance means in the flow to said devices forvarying the pressures as `determined by the first-named resistances,

means for rotating the receiver, means responsive to rotation of the transmitter for complementally varying one set of resistances and thereby inversely varying the pressures on the opposed devices lto cause rotation of the receiver, and means responsive to receiver rotation for complementally varying the other `set of resistances to equalize the opposed pressures on said devices.

2. In a signaling system, the combination of a rotatable transmitter, a remote rotatable receiver, a plurality `of opposed pairs of fluid operable devices connected in couple formation to the re-l ceiver, a source o'f pressure operating fluid, a. multiple channel connection for delivering fluid from said source tothe 'individual devices, means inthe individual channels for variably resisting the ow from said devices and thereby controlling the pressure thereon, `additional means in the individual channels for variably resisting the vflow to said devices, means for rotating the receiver, means responsive to rotation of the transmitter for varying the last-named resistances to vary the pressures Aacting on said devices and thereby cause rotation of the receiver, and means responsive to rotation of the receiver upon movement through an angle equal to the angle of rotation of the transmitter for equalizing the pressure on said devices to stop the receiver.

3. In a gun control mechanism, the combination of a transmitter having a rotatable portion, a sighting apparatus operatively connected to the rotatable portion of the transmitter for rotation thereof: upon movement of the sighting apparatus through la given plane, a gun movable in a4 plane coincident with the plane of movement of thesighting apparatus, a receiver having a rotatableportion to move the gun, a servo-motor operatively connecting the receiver to the gun, al plurality of pairs of opposed fluid operable devices in the receiver, a source of pressure for, delivering fluid continuously to said devices, means .on the transmitter responsive Vto rotation of the rotatable portion of the transmitter for rotating therotatable'portion of the receiver, said means being responsive to rotation of the rotatable portion of the transmitter forv inducing pressure changes in the'fluid acting on said devices to cause rotation of the rotatable portion of Vthe receiver, and means responsive to rotation of the rotatable portionfof the receiver for equalizing said pressures when the receiver portion has movedthrough an angle equal to the movement of4 thetransmitter portion.v y

4. In a signaling system, the combination of a rotatable transmitter, va remotely located rotatable receiver, a plurality of pairs of opposed fiuid operable devices for connecting in couple formation to the receiver to rotate it, a source of pressure operating fluid continuously flowing through said devices, means resisting the flow from said devices to create an operating pressure thereon, additional means for resisting the ilow to said devices, `said last-named means being located in the transmitter, means responsive to the rotation of the transmitter through a predetermined arc to effect a predetermined change in the opposing pressures in each couple, and means responsive to rotation of vthe movable receiver through the same predetermined yarc to equalize the opposed pressures in each couple and to stop the receiver.

5. An hydraulic mechanism for maintaining a remotely located rotatable receiver element in synchronized relation with a rotatable transmitter element comprising a plurality of hydraulic channels, each channel containing a first resistance, a piston, and a second resistance in the order named, a common source of pressure for maintaining a continuous flow through all of said channels, said pistons being mounted in the receiver and arranged in couple formation, a multiple cam device arranged in Contact with said pistons, the number of cams being odd in number with respect to the number of said pistons, each cam having a piston advancing portion and a piston retracting portion whereby an equal pressure on opposed pairs of pistons will tend to hold the cam device at rest, an increase in pressure on one piston over the other of a couple will cause rotation of the cam in a clockwise direction, an increase in pressure on the other piston will cause rotation in a counter-clockwise direction, and means in the transmitter for inducing pressure changes in the receiver to cause thereceiver to move in synchronized relation with the transmitter.

6. In a system for transmitting motion between spaced points, the combination of a rotatable transmitter, a rotatable receiver, a plurality ofhydraulic channels extending from the transmitter to the receiver, said receiver comprising four radial pistons arranged in opposing pairs, a rotatable cam member circumscribing the outer ends of said pistons Yand having a plurality of arcuate-shaped cam portions odd in number with respect to the numbers of said pistons, means connecting said channels to the inner end of said pistons to cause outward movement thereof into contact with said cam portions, independent exhaust channels connected to the respective plstons, resistance means in each channel variable in accordance with the position of the piston for creating variable pressures thereon, said transmitter element being similarly composed and including resistances for varying the pressure in said channels whereby rotation of the transmitter will cause an unbalancing of pressure in the respective pairs of channels to cause rotation of the. receiver7 which rotation will continue until the resistances in the receiver are made equal to the resistances in the transmitter.

7. In a mechanism for transmitting motion between spaced points, the combination of a rotatable transmitter, a rotatable follower, a plurality -of channels extending from the transmitter to Vthe follower, a source of pressure, means to cou- `ple the source of pressure to one end of all of said channels to maintain a continuous flo-w therethrough, movable pistons associated with 16 both ends of all of said channels and subject to the pressure therein, the pistons at one end being connected in pairs to the transmitter, the pistons at the other end being connected in pairs to the follower, one member of each pair opposing the direction of movement of the other member of said pair, whereby when equal hydraulic pres'- sure exists in all of said channels said pistons will be in equilibrium, means for rotating the follower, means responsive to movement of the pistons at the transmitter upon rotation of the transmitter to differentially vary the quantity of iiow in the several channels and thereby create differential pressures therein which will cause unbalance and resultant movement of the pis;- tons at the follower and thus cause rotation of the follower, and means responsive to movement of the last-named pistons to re-establish equal pressures in said channels and thus terminate follower rotation.

8.' Means for maintaining a rotatable follower in synchronized relation with a rotatable transmitter including a plurality of channels and extending from the transmitter to the follower, a source of pressure, means to couple the source of pressure to one end of all of said channels to maintain a continuous flow therethrough, mov,- able pistons associated with both ends of all of said channels and subject to the pressure therein, the pistons at one end being connected in pairs to the transmitter, the pistons at the other end being connected in pairs to the follower, one member of each pair opposing the direction of Amovement of the other member of said pair, whereby when equal hydraulic pressure exists in all of said channels said pistons will be inequilibrium,

' and means for rotating the follower the lastnamed'means being responsive to movement of the pistons at the transmitter upon rotation of the transmitter to differentially vary the quantity of ow in the several channels and thereby create differential pressures therein which will cause unbalance and resultant movement of the pistons at the follower and thus cause rotation of the follower, means responsive to movement of the last-named pistons to reestablish equal pressures in said channels and thus terminate follower 10- tation, and a servonnotor mechanism operable by the follower for amplifying the output torque thereof.

HANSl ERNST.

BERNARD SASSEN.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS

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