US2447707A - Control apparatus for a plurality of motors - Google Patents

Description

Aug. 24, 1948. H. c.-MAY

CONTROL APPARATUS FOR A PLURALITY OF MOTORS Filed July 31, 1945 2 Sheets-Sheet 1 IN VEN TOR. Harry CMay' v BY ATTORNEY Q mm m Gm mm m.

H. C. MAY

Aug. 24, 1948.

2,447,707 CONTROL APPARATUS FOR A PLURALITY OF MOTORS I Filed July 31, 1945 v 2 Sheets- Sheet 2 INVEN TOR Hamy C. May

ATTORNEY Patented Aug. 24, 1948 y;

CONTROL APPARATUS FOR A PLURALITY OF MOTORS Harry G. May,- EastMcKeesport, Pa., assignor to The Westinghouse Air Brake Company, Wilmerding, Pa., a corporation of Pennsylvania Applicationduly a1, 1945, Serial No. 607,926

This invention relates to control apparatus of the type employed to manually control fluid pressure operated motors for obtaining movement in more than one plane of a device such as a gun turret, searchlight or any device which is to be pointed at a particular object. 7

The principal object of the invention is to provide an improved control apparatus oftheabove mentioned type.

Another object of the invention is to provide a control apparatus of the above type which is capable of producing either vertical or horizontal movement, or any combination of the two movements, at any desired rate of speed.

A further object of the invention is to provide, in a control apparatus of the above type employing a motor which is operated in response to fluid under pressure supplied from a continuously driven fluid pressure pump under the control of a manually operated control valve device, means responsive to the flow of fluid permitted by the valve device to condition the pump to automatically increase or decrease the supply of fluid under pressure according to the requirements of the apparatus.

The foregoing and other objects, which will become apparent upon reading this specification in conjunction with the accompanying drawings, may be attained by means of the particular apparatus shown in the various figures wherein:

Fig. 1 is adiagrammatic view, chiefly in section, of a preferred embodiment of the invention;

Fig. 2 is an elevation sectional view taken on the line 2-2 through a portion of the apparatus shown in Fig. 1;

Fig. 3 is a sectional view of the same taken on the line 3-3 in Fig. 1; and

Fig. 4 is a diagrammatic view, partly in section, of a modified form of the invention.

Description As shown in Fig. l of the drawings, the control apparatus may comprise a rotary hydraulicpump a duplex control valve device .2, a rotary hydraulic motor 3, a sump reservoir 4,.- and an actuating cylinder 5.

The rotary hydraulic pump l is of the variable displacement type and comprises a supercharging portion t and a high pressure pump portion 1, both. portions being mounted in a common casing 8. The supercharging portion 6 comprises a pair of hydraulic pump gears 9 operatively mounted in a chamber l formed in the casing 8, the inlet side of the chamber being connected by way of passage and pipe I l and pipe I2 to the sump res- 13 Claims.

lever 3 l.

ervoir 4, and the outlet side of the chamber being connected by way of passages l3 and I4 to an inlet port l5 in a rotary valve seat (not shown) in the high pressure pump portion I.

The high pressure pump portion 1 comprises a drive shaft l6 having formed integrally therewith a cylinder l I provided with a plurality of bores"! 8 and arranged to be rotatably mounted in a chamber 19 in the casing 8, which chamber is connected to the outlet of reservoir 4 by way of pipe l2. The drive shaft I6 is ported so as to effect the proper charging and discharging connections from the bores l8 to the inlet port 15 and an outlet port 20 in the aforementioned rotary valve seat (not shown) which is slidably engaged by' the endof the shaft. Slidably and rotatablymountedinthe bores I8 of the cylinder "l1 are a plurality of pistons 2| which may move outwardly in response to centrifugal force developed by the rotation of the cylinder and also fluid pressure until a beveled edge 22 On the outer end of each piston engages an inner race 23 of a roller bearing 24 which surrounds the cylinder 11.

The bearing 24 is provided with an outer race 25 having two straight and parallel opposite facing outer surfaces so that horizontal movement of the bearing 24 may be guided by caged bearings 26 acting thereon.

For automatically positioning the roller hearing 24 according to the flow of fluid under pressure permitted bythe control valve device 2, the

pump is further provided with an operating mechanism 21, which mechanism comprises a casing 28 mounted by suitable means (not shown) to the left-hand side of the casing 8 of the pump l. Formed in a section of the casing 28 is a chamber 29 open at one end to the chamber l9 and containing an operating stem 30, the left-hand end of which stem engages the outer race 25 of the bearing 24. The other end of the stem is pivotally connected with one end of an unloading Interposed between and operatively engaging the right-hand'wall of the chamber 29 and alspring seat 32 carried on the stem 30 is a [spring-'33 for actuating the bearing 24 to the right for the purpose of increasing the displacement of the pistons 2| as will hereinafter more fully appear. The lever 3| is pivotally mounted at its other and upper end to the casing 28 and is arranged to be engaged intermediate its ends by a piston 34 in such a manner that, when actuated outwardly, the piston 34 will cause the stem 30 to move in a direction away from the bearing 24 and again-st the pressure of the spring 33. The piston 34 is carried in a bore 35 formed in the easing 9.9, the bore being constantly in open communication by way of a passage 36 with a pump delivery passage 31.

At the right-hand side as viewed in Fig. 1, the race 25 is provided with a boss 38 for slidable engagement with a shiftable control cam 89, the vertical movement of which cam causes the race to be shifted horizontally in the bearings 26, thereby cutting the pump into and out of high pressure operation as the demand requires. This cam 88 is carried by a pair of opposed pistons 48 and ll operatively disposed in piston chambers 42 and 93, respectively, the piston 48 and chamber 42 being the larger in diameter for reasons which will appear more fully later. The piston chamber 42 is in constant communication by way of a passage 44 with check valve chambers 46, 41 and 48 above the ball check valves 49, 59 and contained respectively therein, and also by way of passage 44, and a choke 44a to a pipe 45. The piston chamber 43 is connected by way of a passage and pipe 52 to the delivery passage 31 and to a chamber 53 in the casing 8, which chamber contains a check valve 54 biased toward its seat against the fluid pressure in passage I3 by a light spring 55.

The duplex control valve device 2 is provided for the purpose of controlling the flow of fluid under pressure supplied from the pump I to the rotary hydraulic motor 3 and the actuating cylinder 5 and the discharge of fluid therefrom. This control valve device 2 may be of the same general type as that shown and described in my application Serial No. 496,868, filed in the United States Patent O-fiice, July 31, 1943, and assigned.

to the assignee of the present invention.

The duplex control valve device 2 may com prise a lower body casing 56 and an upper body casing 51, the body casing 56 being provided with a centralbore 58 which is closed at its upper end by a wall 59 and at its lower end by a cap member 68 which may be secured to the bottom of the casing 56 by any suitable means (not shown). As shown in Figs. 1 and'2, there is provided in the casing 56 near its upper end a port 6| which is open to the bore58 and is connected by way of passage and pipe 62 to a chamber 63 at one side of a piston 64 in the actuating cylinder'5. Near .its lower end the casing 56 is provided with a similar port 65 which is also open to the bore 58 and is connected by way of a passage and pipe 66 to a chamber 61 at the other side of the piston 54 in the actuating cylinder 5. In vertical alignment with the ports 6| and 65 and midway between them a supply port 68 is provided in the casing 56, which port is open to the bore 58 and is connected to the delivery passage 31 of the high pressure pump portion 1 of the pump by way of the passage 69 and pipe 52. To the left of the supply port 68 as viewed in Figs. 1 and 3 the casing 56 is provided with a port through which fluid under pressure may be supplied by way of passage and pipe 1| to the rotary motor 8 to eifect the operation thereof in one direction. For efiecting the operation of the motor 3 in the opposite direction, a port 12 is similarly provided in the casing to the right of the supply port 68 and is connected to the motor 3 by way of a passage'and pipe 13. For reasons which will hereinafter more fully appear, the pipes H and 13 are connected to the under sides of the ball check valves 5| and 49, respectively, in the pump by way of the respective pipes 14 and 15.

For controlling the flow of fluid under pressure through the aforementioned ports a valve 16 is operatively mounted in the bore 58 for both rotary and vertical movement therein. This valve 16 is provided with a central bore or discharge passage 11 which is connected to the delivery passage |3 of the supercharging portion 6 of the pump I by way of the bore 58 and a discharge passage. and pipe 18. For effecting communication between this discharge passage 11 and either chamber 63 or 61 of the actuating cylinder 5, the valve 16 is provided with a radially extending through passage 19 which may be brought into registration with the port 6| by downward linear movement of the valve 16 and also a radially extending through passage and port 80 which may be brought into registration with the port 65 by upward linear movement of the valve 16. A sim-- ilar passage and port 8| may be brought into registration with the port 19 by horizontal rotation of the valve 16 to the right and another similar passage and port 82 may register with the port 12 upon horizontal rotation of the valve 16 to the left, thereby controlling the discharge of fluid from the rotary motor 3. For the control of the flow of fluid under pressure to the actuating cylinder 5 or the rotary motor 3, or both, the valve 16 is provided with a cavity 83 which is in constant open communication with the supply port 68 in the bore 58, which port, as previously mentioned, is connected by way of pipe 69 to the deliverypassage 21 of the pump This cavity 83 is so constructed and arranged that when fluid is discharged from one side of the cylinder 5 or the motor 3, the cavity 83 will become effective to supply fluid under pressure to the other side to eifect the operation of that device.

The upper body casing 51 is retained in rotatable relation to the lower body casing 56 by means of a disc member 84 and the wall 59 of the casing 56 to which the disc member may be rigidly secured by any suitable means such as cap screws 84a. Formed integrally with the disc member 84 and interposed between a pair of oppositely disposed spring actuated plungers 85 and 86 carried in the casing 51 is an upright ear the valve 16 said valve is provided with an integral stem 88 which extends through suitable apertures in'the casing 56 and the disc member 64 to make within the casing 51 a positive connection with one end of a link 89. This link 89 makes at its other end a pivotal connection with a pin 99 carried by a shaft 9| which is horizontally and rotatably mounted in the casing 51. Formed integrally with the shaft 9| and interposed between a pair of opposed spring actuated plungers 92 and 93 disposed at right angles to the shaft 9| is an upright lug 94 against which the plungers 92 and 93 may react to yieldably urge the shaft to rotate toward a central neutral position. The shaft extends through suitable bearings 95 in the casing 51 and at each end terminates in a suitable handle 96, whereby the shaft may be rotated axially to impart longitudinal movement to the valve 16 and whereby the shaft may be rotated end for end to impart rotary movement to the valve 16.

Operation Let it now be assumed that this control apparatus is being used in connection with a gun turret, that the rotary motor 3 is utilized to obproper. elevation of the gun, and that both the turret traverse and the gun elevation are obtained through the manipulation of the control valve device 2 by the gunner. It will also be assumed that the various parts associated with the several devices described are in the position in which they are shown in Fig. l, and that the pump is being driven at a constant speed by an electric motor (not shown) or other power means.

Fluid will be supplied from the sump reservoir 4 by way of pipe l2 and inlet passage H to chamber ID in the supercharging portion 6 of the pump I. The gears will be rotated in the directions to supply fluid unofier pressure to the inlet port l5 of the high pressure pump portion 1 by way of passages I3 and M. This fluid under pressure in the passage |3 will also be supplied at a low degree of pressure past the check valve 54 and by way of passage 3! to provide a cushion and thereby obtain smoother performance when the pump is first put into operation. Fluid under pressure in passage l3 will also be supplied by way of pipe 18 to a chamber I in a check valve device ||l| mounted in the sump reservoir 4. Should the fluid pressure in the chamber I00 exceed a selected degree such as '75 pounds per square inch, the excess pressure will cause a piston valve I02 to move to its unseated position against the opposing pressure of a spring I03 thereby permitting the excess fluid under pressure to pass to the sump until the pressure is reduced to 75 pounds.

It will be understood that the bearing 24 will, in the normal position in which it is shown in Fig. 1, be disposed in the chamber I9 so that its center lies slightly to the right of the center of the shaft I6 and the cylinder I1. In this normal position the pump is conditioned for the delivery of fluid at a pressure of 30! pounds per square inch. As the cylinder I1 is rotated the pistons 2| are held by centrifugal force of the rotation and fluid pressure in engagement with the inner periphery of the inner race 23 of the bearing 24. Because of the aforementioned eccentricity between the bearing 24 and the cylinder the pistons 2| will be permitted to move outwardly in the lower half of their path of travel and forced inwardly in the upper half of their path of travel. While the pistons are moving outwardly the horse is in which they are mounted are connected by way of ports I04 in the shaft It to the inlet port !5 in the rotary valve seat (not shown) and. while the pistons are moving inwardly the bores |8 are connected by way of the ports |04 to the outlet port 26. Thus fluid will normally flow from the supercharging portion 6 at a pressure of 75 pounds by way of passages 13 and I4, inlet port l5, ports I04 to the bores It! in the cylinder l1 and thence by way of ports I04, outlet port 20', and passage 31 to ipe 52, at a pressure of 300 pounds.

It should be understood that although fluid under pressure in passage 31 is communicated by way of pipe 52 to the piston chamber 43 the relation of the areas of the pistons 46 and 4| is such that the 300 pounds pressure in the piston chamber 43 acting on the piston 4| will balance with the previously mentioned '75 pounds fluid pressure in the chamber 42 acting on the piston 40. Under this balanced condition the cam 39 will be maintained in the position in which it is shown in Fig. 1.

Now if the gunner wishes to decrease the angle of elevation of the gun, he will rotate the hdl l llte t e contr l valve device 2 in a counterclockwise direction from the neutral position in which it is shown in Fig. l of the drawings. This movement will cause the shaft 9| to also rotate counter-clockwise about its axis against the opposing pressure exerted by a spring I05 acting through the medium of the plunger 92 on the lug 94 which is integral with the shaft. The shaft 9| will act through the medium of the pin 90, link 89, and stem 88 of the valve '56 to move said valve in a vertically downward direction. Downward movement of the valve 16 may be continued until the valve is brought to a stop by the bottom of the valve engaging the inner surface of the cap member 60.

As the valve 16 is moved downwardly the supply port 68 is connected to the chamber 61 in the actuating cylinder 5 by way of port 65 and passage and pipe 66. At the same time the chamber 63 at the opposite side of the piston 64 in the actuating cylinder 5 is connected to the discharge pipe 18 by way of pipe 62, ports 6| and 16, and discharge passage Tl. With these communications established, fluid under pressure is supplied to chamber 61 at the lower side of the piston 64 in the actuating cylinder 5 and fluid under pressure at the upper side of piston 64 is discharged so that the piston 64 is caused to move upwardly from the position. This upward movement of the piston will cause a shaft I36 associated with the cylinder to rotate in a direction for decreasing the angle of elevation of the gun. When the gunner releases his grip on the handle 96 of the control valve device 2, the spring I05, acting through the medium of the plunger 92 and the lug 94 of the shaft 9|, causes the shaft to rotate in a clockwise direction and thereby return the handle 96 to its neutral position. At the same time the valve I6 is caused to move upwardly to its neutral position, in which position the ports 6| and 65 in the casing 56 are lapped. Further flow of fluid under pressure to chamber 61 and discharge of fluid under pressure from the chamber 63 is cut off, so that the piston 64 will be maintained in its adjusted position.

Now when the gunner wishes to increase the angle of elevation of the gun, the necessary downward movement of the piston is obtained by rotating the handle 96 of the control valve device 2 from its neutral position in a clockwise direction about the axis of the shaft 9| as viewed in Fig. 1. Clockwise rotation of the shaft 9| causes the lug 94 to actuate the plunger 93 against the opposing pressure of a spring WI and at the same time acts through the medium of the link 89 and stem 88 to impart upward movement to the valve 16. Upward movement of the valve 16 connects the supply port 68 in the casing 56 of the control valve device 2 with the chamber 63 at the upper side of the piston 64 in the actuating cylinder 5 by way of cavity 83, port 6| and pipe 62 while connecting the chamber 61 at the opposite side of the piston 64, to the discharge pipe 18 by way of pipe 66, ports 65 and 80, and discharge passage 11. With these communications established, the pressure of fluid in chamber 63 is increased and the pressure of fluid in chamber 61 is decreased, thus causing the piston 64 to move downwardly. When the desired elevation of the gun is reached, the gunner may release his grip on the handle 96 and. the handle, together with the shaft 9|, is rotated counter-clockwise to neutral position by the pressure of the spring |0| acting through the medium of the plunger 93 and the lug 94. The pressure of the spring also acts through the medium of the shaft 9|, link 89 and stem 88 to move the valve 16 downwardly to its neutral position thereby lapping the ports 6| and 65 in the casing 56 and again cutting off communication with the chambers 63 and 61 in the actuating cylinder 5, so that the piston 64, and therefore the gun, will be held in the desired position.

It will be understood that during all of the operations previously described herein, the pump I is operated continuously in its normal position in which it is shown, or to the right thereof, to thereby maintain a fluid pressure of 300 pounds in the delivery passage 31 and pipe 52 in a manner now to be described. It will also be understood that a pressure of 300 pounds is sufficient to operate the actuating cylinder any time when a change in the elevation of the gun is desired.

It will be apparent that when the flow of fluid under pressure to the control valve device 2 is out off, the pressure of fluid in the pipe 52, and likewise in the connected piston chamber 43, will rise rapidly if the output of the pump I continues at the same rate. It will be remembered that the the pressure of fluid in chamber 42 acting downwardly on the piston All remains constant at 75 pounds against which 300 pounds fluid pressure acting upwardly on the piston M is balanced. Consequently, when the fluid pressure in chamber 43 increases above 300 pounds the pistons 48 and t! together with the cam member 39 will be caused thereby to move upwardly. Since cam member 39 extends gradually inwardly toward its lower end, upward movement of the cam member, acting through the medium of the boss 38, will cause the bearing 24 to be shifted toward the left against the opposing pressure of the spring 33, moving the bearing toward a position of concentric relation with the cylinder I1 and thereby reducing the output of the pump. This upward movement will continue until the delivery pressure is reduced to 300 pounds again and may be such that the pump is practically cut out. It will thus be seen that this combination of the pistons 40 and 4| and cam member 39 with the bearin 24 and spring 33 acts as a governor for the pump so as to limit the pressure of its normal output to 300 pounds.

The gunner may also efiect the traverse of the gun turret in either direction by swinging the handles 95 of the control valve device 2 in arcs of 1 a circle about the vertical axis of said device in the same direction as that desired for movement of the gun turret. When the gunner wishes to effect a traverse of the gun turret to the right, for example, he will swing the handles 96 in a clockwise direction from the neutral position in which they are shown in Figs. 1 and 2. This movement of the handles causes the shaft 9| and thereby'the upper body casing 51 to rotate in the same direction.

As the upper body casing 51 is thus rotated, it moves relative to the lug 8'! carried by the disc member 84 since the disc member is, as hereinbefore described, rigidly secured to the lower body casing 56. This rotative movement of the casing 51 causes the plunger 86 at the right-hand side of the lug 81 to move inwardly against the opposing pressure of a spring I88 and also acts through the medium of. the shaft 9|, pin 90, link 89 and stem 88 torotate the valve 15 in-a clockwise direction about its aXis as viewed in Fig. 3. By referring to Fig. 3 it will be apparent that such movement of the valve 18 will establish communi cation between the supply port 68 and the passage and pipe 13 by way of the cavity 83 in the valve and port 12 in the casing. At the same time said valve establishes communication between the pipe 1| and the discharge pipe 18 by way of port 18 in the casing 56, discharge port 8| and the discharge passage 11 in the valve. With these communications established, fluid under pressure is supplied from the delivery passage 31 in the pump l by way of pipe 52, supply port 68, cavity 83, port 12, and passage and pipe 13 to the upper side of the motor 3 while fluid under pressure is discharged from the lower side of said motor by way of pipe and passage 1|, ports 10 and 3|, discharge passage 11 and discharge pipe 18. This flow of fluid under pressure will cause a shaft I89 of the motor 3 to rotate in a direction which, through suitable gear means (not shown) will sheet the traverse of the gun turret to the right.

When the turret reaches the desired position, the gunner releases his grip on the handles 96 and the spring I08 exerts, through the medium of the plunger 36, a pressure on the lug 81 of the disc member 84, causing the upper body casing 51 in which it is mounted and thereby the shaft 9| and attached handles 96 to rotate in a counter-clockwise direction toward the horizontal neutral position. With this movement of the shaft 9!, the valve 18 is rotated through the medium of the pin 90, link 89 and stem 88, in a counter-clockwise direction to its horizontal neutral position in which position the ports 10 and 12 in the casing are lapped. With communication with the motor 3 thus cut off the gun turret will be held in its newly acquired position.

It should here be understood that, the weight of the gun turret being many times greater than that of the gun, the work required to effect the traverse of the gun turret will likewise be many times greater than that required to change the elevation of the gun. Since it is highly desirable for reasons of economy of space tohave a small motor or power means, it becomes necessary to use fluid at a high degree of pressure, such as 1,800 pounds, in order to effect the traverse of the gun turret promptly and quickly. Control means are accordingly provided for automatically cutting the pump into high pressure operation by increasing its piston displacement when the gunner wishes to effect the traverse of the gun turret.

It should be noted, therefore, that the pipe 13 is also connected by way of pipe 15 to the under side of the ball check valve 49 in chamber 43 which chamber is connected by way of passage M to the piston chamber 42. Thus, when fluid under pressure at a degree of 300 pounds is supplied to pipe 13 as a result of the manipulation of the control valve device 2 as just previously described, fluid at a pressure of 300 pounds also flows by way of pipe 15 past ball check valve 49 and through passage 44 to the top of piston 40 in chamber 42. Although fluid at a pressure of 300 pounds is also supplied from the passage 31 to the face of th piston 41' in chamber 43 by way of pipe 52 in opposition to the downward pressure acting on the piston 48, the latter pressure will prevail because, as previously noted, the effective area of the piston 40 is greater than that of the piston 4!. In response to the preponderance of downward pressure, the pistons 40 and 4| will move downwardly, thereby causing the cam member 39 to be actuated downwardly to a position defined by contact between the piston 4| and a cap member H0 closing the bottom of the chamber 43. In consequence of the pressure of the spring 33 acting on the bearing 24 through the medium of the spring seat 32 and stem 30 to maintain the boss 38 of said bearing in slidable contact with the graduated surface III of the cam 39, the downward movement of the cam will permit the bearing race 24 to be shifted to the right as viewed in Fig. 1.

It will here be understood that if the center of the bearing 24 coincides with the center of the shaft l6 and cylinder [1 there will be no axial reciprocating movement of the pistons 2| in the bores l8. Consequently the pump portion 1 will not produce any flow of fluid under pressure.

However, if the center of the bearing '24 is displaced to the right as viewed in Fig. 1 each of the pistons 2| will make one reciprocatory cycle for each revolution of the cylinder 1. The displacement of each piston 2| is substantially equivalent to the amount the center of the bearing 24 is displaced from the center of the shaft |1. It will be apparent, therefore, that when the bearing 24 is shifted to the right in the manner hereinbefore described, the flow of fluid under pressure to the delivery passage 31 will be increased in proportion to the degree of displacement of the center of the bearing to the right of the center of the shaft.

It should be further noted that by reason of the tapered ports in the control valve device 2, the speed of operation of the motor 3 and cylinder 5 and therefore the volumetric requirements will be varied. Since the pump is operated at a constant speed, it follows that the pressure of fluid in the delivery pipe 31 will vary inversely to the flow of fluid away from the pipe. This varying pressure would prevent the gunner from anticipating with any degree of certainty how the motor 3 was going to respond to a, certain manipulation of the control valve device 2. Therefore, the operating mechanism 21 of the pump is provided to insure a constant 1,800 pound fluid pressure, and no more, being available for operation of the motor 3, and thus obviate the above undesirable condition.

Fluid under pressure in the passage 31 will flow by way of passage 36 to the face of the piston 34 in the bore 35, tending to move the piston to the left as viewed in Fig. l and rotate the lever 3| about its upper end. However, this movement is opposed by the presure of the spring 33 acting on the lower end of the lever 3| through the medium of the spring seat 32 and stem 30. When the fluid pressure in the bore 35 exceeds 1800 pounds, the pressure acting on the piston will cause the piston to move toward the left. This movement will cause the lever 3| to rotate about its upper end in a clockwise direction, thereby moving the stem 30 against the opposing pressure of the spring 33 acting through the medium of the seat 32.

It should be explained that in a pump structure of the type described in connection with pump portion 1 the bearing 24 has an inherent tendency to return to its non-operative position, which in this example would be toward the left. Consequently, the bearing race 25 will follow the movement of the stem 30 to the left, thereby reducing the displacement of the pump portion 1. The reduced displacement will reduce the pressure in the delivery passage 31 and in the bore 35, which will continue until the piston 34 and the spring 33 reach a, state of equilibrium. Should the pressure in the bore 35 be further reduced, the spring will act through the medium of the stem 30 to shift the bearing '24 to the right and thereby v increase the pump displacement.

When the gunner released his grip, the spring I08, acting by means of the plunger 86 and the lug 81 of the disc member 84, caused the upper body casing 51 and thereby the shaft 9| and attached handles 95 to rot-ate in a counter-clockwise direction until it reached its neutral position. As the shaft BI is rotated end-for-end in a counter-clockwise direction, the valve 16 is also rotated in a counter-clockwise direction through the medium of a pin 90, a link 89 and stem 08 to its neutral position, in which position the ports 10 and 12 in the casing 56 are lapped. With these ports lapped, the supply of fluid under pressure to and the release of fluid under pressure from the motor 3 is cut off and the gun turret will be held in its latest assumed position.

When the supply of fluid under pressure to the pipe 13 is cut off, the flow of fluid under pressure to the chamber 42 by way of pipe 15, check valve chamber 46 and passage 44 is likewise cut off. Since the chamber 42 is always open by way of the choke 44a and pipe 45 to the discharge pipe 18, fluid under high pressure in chamber 42 will flow to pipe 18 and thence past check valve I02 (set at '75 pounds) in chamber I00 to the sump in reservoir 4.

The fluid at high pressure in delivery passage 31 will still be communicated to the piston chamber '43 by way of the pipe and passage 52. As the pressure acting in a downward direction on the piston 40 is gradually reduced, the 1800 pound pressure acting upwardly on the piston 4| will become sufficient to actuate the cam 39 upward toward the position in which it is shown in Fig. 1. Upward movement of the cam 39 will act through the medium of the boss 38 to shift the bearing 24 to the left against the opposing pressure of the spring 30 and toward its normal position in which it is shown in Fig. 1.

When the gunner wishes the gun turret to move to the left,-he may swing the handles 90 in a counter-clockwise direction'from the neutral position in which they are shown, thereby acting through the medium of the shaft 9|, to which they are attached, to rotate the upper body casing 51 in a counter-clockwise direction. This rotary movement relative to the fixed lug 81 will cause the plunger 85 at the left-hand side of the lug to be moved inwardly against the pressure of aspring I I2.

Counter-clockwise rotation of the asing 51 also eifects through the medium of the shaft 9|, pin 90, link 89 and stem 88 the counter-clockwise rotation of the valve 16. As best shown in Fig. 3 this movement of the valve 16 wil1 establish communication between the supply port 63 and the passage and pipe 1| by way of the cavity 83 in the valve 15 and port 10 in the casing 56. At the same time said valve establishes communication between the pipe 13 and discharge pipe '18 by Way of port 12 in the casing 56, discharge port 82 and the discharge passage 11 in the valve 16. Thus fluid under pressure in the delivery passage 31 may be supplied by way of pipe 52, supply port 68, cavity 83, port 10, and passage and pipe 1| to the lower side of the motor 3 while fluid under pressure is discharged from the upper side of the motor 3 by way of pipe and passage 13, ports 12 and 82, discharge passage 11 and discharge pipe 18. This flow of fluid under pressure will cause the shaft I09 of the motor to rotate in a direction which will efiect the traverse of the gun turret to the left.

When the turret reaches the desired position, the gunner will permit the spring H2, exerting through the medium of the plunger 85 a pressure on the lug 81 f the disc member 84, to effect the clockwise rotation of the casing 51, and thereby the shaft BI and handles 98 attached thereto, to the neutral position in which they are shown. This movement of the shaft 9| causes the valve 16 to be rotated through the medium of pin 90, link 89 and stem 88 clockwise to neutral position, in which position the ports 70 and I2 in the casing are again lapped.

It will be noted that the pipe II is also connected by way of pipe I4 to the under side of the ball check valve 5| in chamber 48 which chamber is also connected by way of passage 44 to the piston chamber 42. Thus, when fluid at a pressure of 300 pounds is supplied to the pipe I! by manipuation of the control valve device 2, fluid at a pressure of 300 pounds also flows by way of pipe 74 past ball check valve 5I and through passage 44 to the top of piston 40 in chamber 42. The pump I will again be cut into high pressure operation to deliver fluid at a pressure of 1800 pounds in the same manner as previously described in connection with supplying fluid under pressure to pipe 13 to effect the traverse of the turret to the right.

It is thus made apparent that when fluid at a pressure of 300 pounds is supplied to either side of the motor 3, this fluid pressure will also be communicated to the face of the piston 40 in chamber 42 to efiect thereby the operation of the pump to supply fluid at a pressure of 1800 pounds. When the flow of fluid under pressure to motor 3 is cut off the pump will return automatically to its normal position in which fluid under pressure is supplied at 300 pounds. When the actuating cylinder 5 is operated, the pump I will remain in normal position, but when the motor 3 is brought into operation, either alone or together with the cylinder 5, the pump I will automatically move to a high pressure position to supply fluid at a pressure of 1800 pounds.

The actuating cylinder 5 can'be operated by the 300 pounds or 1800 pounds pressure, either being suificient for its complete operation. Obviously, by permitting the pump to operate normally at 300 pounds pressure except when moving the turret, a more economical operation may be obtained.

In certain installations it has been found highly desirable to have a second control station at the comman-ders post, from which station the commander would be able when the occasion arose to intercept the gunners control and as sume the control himself. To attain this result there has been provided in this invention an additional duplex control valve device which may be connected in parallel with the duplex control valve device 2, and has in addition, an intercepting valve device interposed between the valve device 2 and the motor 3 and cylinder 5 for manual operation to cut off said communication.

Referring now to Fig. 4 of the drawings, there is device comprises a duplex control portion I2I, which portion is shown only in outline since the structure and function are the same as those for the duplex control valve device 2. The control portion I2I is arranged to be supplied with fluid under pressure by way of pipe 52 as is valve device 2. The control portion is also arranged to shown a duplex control valve device I28, which tion. At its upper supply fluid under cylinder 5 by way of either a pipe I22 or a pipe I23 while discharging fiuid under pressure from said cylinder by way of the other pipe. These pipes I22 and I23 are associated with control portion I2I in the same manner as are pipes 62 and 68, respectively, with valve device 2. The control portion is further arranged to supply fluid under pressure to the motor 3 by way of either a pipe I24 or a pipe I25 while discharging fluid under pressure from said motor by way of the other pipe. These pipes bear the same relation to control portion I2I as do pipes II and 73, respectively, to the control valve device 2.

Secured to the bottom of the casing for the duplex control portion I2I by any suitable means (not shown) is an intercepting valve device I26, which device comprises a casing I2! having formed therein a plurality of valve chambers I28, I29, I30 and I3I and cam chamber I32.

Operatively mounted in the chamber I28, which is in constant open communication by way of the pipe I24 with the motor 3, is a valve I33 which controls communication between said chamber and pipe and passage 'II connecting with the control valve device 2. Interposed between and operatively engaging the valve I33 and a cap nut I34 closing the bottom of chamber I28 is a spring I35 which constantly urges the valve upwardly toward its seated position. At its upper end the valve I33 terminates in a stem I 36 which extends upwardly through a suitable opening in the casing I 27 into the cam chamber I32 where it may be engaged by a cam surface I31 of a slidable cam member I38 so as to retain the valve in its unseated position in which it is shown in Fig. 4.

Operatively mounted in the valve chamber I29, which is in constant open communication by way of pipe I 25 with the motor 3, is a valve I39 which controls communication between said chamber and pipe and passage I3 connecting with the control valve device 2. Interposed between and operatively engaging the valve I39 and a cap nut I40 closing the bottom of the chamber is a spring I4I which constantly urges the valve in an upward direction toward its seated position. At its upper end the valve I 39 terminates in a stem I42'which extends upwardly through a suitable opening in the casing IZ'I into the cam chamber I32 where it may be engaged by a cam surface I43 of the cam member I38 so as to also actuate the valve I 39 to its unseated position in which position it is shown in Fig. 4.

Operatively mounted in the valve chamber I 30, which is in constant open communication by way of pipe 66 with the control valve device 2, is a valve I44 which controls communication between said chamber and pipe and passage I23 which connects with the actuating cylinder 5. Interposed between and operatively engaging the valve I44 and a cap nut I45 closing the lower end of chamber I30 is a spring I46 which constantly urges the valve upwardly toward its seated posiend, the valve I44 terminates in a stem I4! which extends upwardly through a suitable opening in the casing I21 into the cam chamber I32 where it may be engaged by a cam surface I48 of the cam member I38 so as to also actuate the valve I 44 to its unseated position in which position it is shown in Fig. 4.

Operatively mounted in the chamber I3I, which is in constant open communication by way of pipe 82 with the control valve device 2, is a valve I49 which controls communication between pressure to the actuating said chamber and pipe and passage I22 which connects with the actuating cylinder 5. Interposed between and operatively engaging the valve I49 and a cap nut I50 closing the lower end of the chamber I31 is a spring I! which constantly urges the valve upwardly ,toward its seated position. At its upper end the valve- I49 terminates in a stem I52 which extends upwardly through a suitable opening in the casing I21 intothe'cam chamber I32 where it may be engaged by a cam,

surface I53 of the cam member I38 so as to actuate the valve I49 to its unseated position in which position it is shown in Fig. 4.

Thus it will be seen upon referring to Fig. 4

that, when the intercepting. valve device I26 is in its normal position in which it is shown, fluid under pressure may flow between the control valve device 2 and the motor 3 in one direction by which it is. shown, the gunner may, by the manipulation of control valve device 2 as previously described, control the traverse of the gun turret and the elevation of the gun.

Now if the commander wishes to cut off the gunners control and assume control himself he may move the cam member I38 toward the right,

as viewed in Fig. 4, by means of handle I54 rigidly secured'to the cam member, thereby moving the cam surfaces I31, I43, I48 and I53 relative to the,

valve stems I36, I42, I41 and I52, respectively, so

that the valves may be caused to seat. The spring I will be permitted to actuate the valve I33 upwardly to its seat while spring I4I will be permitted to actuate the valve I33 to its seat. .At the same time spring I46 will move valve .144 to its seat and valve I49 will be seated by the pressure of the spring I5I. Since, as previously noted, the duplex-control portion I2I is in constantly open communication with the motor. .3

and the actuating cylinder 5 by way of plpesl22;

I23, I24 and I25, it follows that thecommander may now exercise, by means of the controlportion I2 I, the same control over the gun and turret as the gunner had previously done byrnanipulation of the control Valve device 2 hereinbefore described. Since the valves I33, I39, I44 and M9. are all seated, all control communications between the control valve device 2 are interrupted and movement of the entirely ineffective.

When'the commander wishes to turn the conhandles 95 thereof will be trol back to the gunner he may do so by moving:

the handle I54 and thereby the cam surfaces I31,

I43, Ma and I53 of the cam member sa to the left. This movement will act through the me-- dium of stems I36, I42, I41 and I52 to cause their respective valves I33, I39, I44 and I49 to move downwardly out of their seated positions against. the opposing pressures of the springs I35, I4I, I45 I and I5I, respectively. With these valves unseated, the communications by which the gunner may control the operation of the motor 3 and actuating cylinder 5 will again be established.

Having now described my invention, .what I claim as new and ent is: I

desire to secureby Letters Pat- 1. In a rotary fluid pressure pump having a rotative portion and a non-rotative portion surroundingsaid rotative portion and movable into eccentric relation therewith, said non-rotative portion being shiftable to increase the degree of said eccentricity and thereby the ouput of said pump, the combination of constant pressure means for shifting said non-rotative portion in a direction for increasing the degree of eccentricity, a cam member having one position for limiting said shifting to a certain low predetermined degree andshiftable toanother position to limit said shifting to a certain predetermined higher degree, and a movable abutment positively connected to said constant pressure means responsive to the pressure of fluid delivered by said pump to directly oppose said constant pressure means and counter-balance the same when a certain predetermined pressure of fluid is delivered.

2.13 constant speed fluid pressure pump comprising in combination a rotatable portion, a bearing portion having a norma1 position relative to said rotatable portion and being shiftable therefrom to another position for increasing the displacement of said pump, a spring biasin said bearing portion toward said other position, a cam member for defining the movement of said bearing portion in. response to the pressure of said spring, said cam member having a normal position in which said bearing portion is located in its normal position andbeing movable therefrom to tion relative to said rotatable portion and being shiftable therefrom to another position for increasing the displacement of said pump, a spring biasing said bearing portion toward said other position, a cam member for defining the movement of said bearing portion in response to the pressure of said spring, said cam member having a normal position in which said bearing portion is located in its normal position and being movable therefrom to a position in which said spring is permitted to shift said bearing portion to said other position, a relatively large piston which will respond to the pressure of fluid supplied from said pump to move said cam member out of its normal position, means for supplying fluid under pressure from said pump to said piston, means for cutting off the supply of fluid under pressure to said piston from said pump, means for reducing the pressure of fluid acting on said pistonwhen'the supply from said pump is cut off, and a relatively small piston subject at all times to the pressure of fluid supplied by said pump and responsive thereto to move said cam member to its normal position when the pressure of fluid'acting on the first mentioned piston has been substantially reduced.

4. A control system for the manual control of fluid pressure operated motors for obtaining movement of a part in more than one plane, in combination, one motor responsive to fluid under pressure above a certain low degree to move said part in one plane; another-motor responsive to fluid at a pressure of a certain predetermined higher degree to move said part in another plane; a pump driven at a constant speed for supplying fluid under pressure to said motors; a control valve device interposed between said pump and said motors for controlling the supply of fluid under pressure to said motors; a second control valve device having connections in parallel with said first control valve device; and an intercepting valve device mounted on said second control valve device comprising a plurality of poppet valves controlling communication between the first mentioned control valve device and said motors, said valves being arranged to be actuated to their seated positions by spring pressure, cam member arranged to slidably engage the stems of said valves and shiftable relative thereto for actuating said valves out of their seated positions, and means for shifting said cam member; said pump comprising a rotative portion, a non-rotative portion having one position for effecting the opera-- tion of the pump to supply fluid under pressure at a degree sufiicient to operate said one motor and being movable to another position for effecting the operation of the pump to supply fluid under pressure at a certain predetermined higher degree to operate said other motor, and means normally causing said non-rotative portion to assume said one position and responsive to the pressure of fluid supplied to said other motor to cause said non-rotative portion to shift to said other position.

5. A rotary pump arrangement comprising a supercharging portion, a high pressure pump portion, a member to be shifted to vary the output of the pump portion according to the distance the member is shifted, movable means operative for effecting the shifting of said member, said means comprising a small piston subject at all times to the high pressure of fluid delivered by said high pressure pump portion and also comprising a larger piston normally subject totherelatively low pressure of fluid delivered bysaid supercharging portion acting in opposition to pressure of fluid on said small piston and responsive to an increase in the pressure of fluid acting thereon to shift said member for increased output of the pump portion, and means operative to effect the flow of fluid under pressure from said high pressure pump portion to said larger piston to thereby increase the pressure of fluid acting on said larger piston.

6. A rotary pump arrangement comprising a supercharging portion, a high pressure pump portion, a member to be shifted to vary the output of the pump portion according to the distance the member is shifted, movable means operative for effecting the shifting of said member, said means comprising a small piston subject at all times to the high pressure of fluid delivered by said high pressure pump portion and also com prising a larger piston normally subject tothe relatively low pressure of fluid delivered by saidsupercharging portion acting in opposition to pressure of fluid on said small piston and responsive to an increase in the pressure of fluid acting thereon to shift said memberfor increasedoutput of the pump portion, means operative to effect the flow of fluid under high pressure from said high pressure pump portion to said larger piston to thereby increase the pressure of fluid acting on said larger piston, and means for re-- ducing the pressure acting on said larger piston to the relatively low pressure of fluid deliveredb'y said supercharging portion.-

7. A fluid pressure pump equipment comprising a high pressure pump variously conditionable to deliver fluid at various high pressures, a supercharger operative to deliver fluid at a relatively low pressure to said pump, means operative to condition said pump to vary the pressure of fluid delivered thereby, said means comprising a piston of small diameter and subjected at all times to the high pressure of fluid delivered by said pump and also comprising a piston of larger diameter normally subjected to the relatively low pressure of fluid delivered by said supercharger acting in opposition to the pressure of fluid acting on said small piston, and said means being responsive to an increase in the pressure of fluid acting upon said piston of larger diameter to condition said pump to operate to increase the pressure of fluid delivered thereby, and means operative to effect the flow of fluid under high pressure from said pump to said piston of larger diameter to effect the operation of the first said means.

8. A fluid pressure pump equipment comprising a high pressure pump variously conditionable to deliver fluid at various high pressures, a supercharger operative to deliver fluid at a relatively low pressure to said pump, means operative to condition said pump to vary the pressure of fluid delivered thereby, said means comprising a piston of small diameter and subjected at all times to the high pressure of fluid delivered by said pump and also comprising a piston of larger diameter normally subjected to the'relatively low pressure of fluid delivered by said supercharger acting in opposition to' the pressure of fluid on said small piston, and said means being responsive to an increase in the pressure of fluid acting upon said piston: of larger diameter to condition said pump to operate to increase the pressure of fluid delivered thereby, control means having at least two control positions and operative to one control position to effect the flow of fluid under high pressure from said pump to act on said piston of larger diameter, and operative to its other control position to cut off the flow of fluid from said pump to said piston of larger diameter, and a choked communication always open to the fluid delivery side of said supercharger through which fluid. acting upon the larger piston flows and thereby effecting a reduction in the pressure'of fluidacting upon the larger piston when said control means is moved from its said one control position toits said other control position.

9. A fluid pressu-re pump equipment comprising a high pressure pump variously conditionable to deliver fluid at various high pressures, a supercharger operative to deliver fluid at a relatively low pressure tosaid pump, means operative to condition said'pump to vary the pressure of fluid delivered thereby, said means comprising a piston of small diameter and subjected at all times to the high pressure of fluid delivered by said pump and also comprising a piston of larger diameter normally subjected to the relatively low pressure of fluid delivered by said supercharger acting in opposition to pressure of fluid on said small piston, and said means being responsive to an increase in the pressure of fluid acting upon said piston of larger diameter to condition said pump to operateto increase the pressure of fluid delivered thereby, control means having at least two control positions and operative to one control position to effect the flow of fluid under high pressure from said pump to act on said piston of larger diameter, and operative to its other control position to cut off the flow of fluid from said pump to said piston of larger diameter, and means effective incident to the operation of said control means from its said one control position to its said other control position for reducing the pressure of fluid acting upon said piston of larger diameter to the pressure of fluid delivered by said supercharger.

10. A fluid pressure pump equipment comprising a high pressure pump variously conditionable to deliver fluid at various high pressures, a supercharger operative to deliver fiuid at a relatively low pressure to said pump, and means operative to condition said pump to limit the pressure of fluid normally delivered by said pump, said means comprising a piston 01 small diameter subjected at all times to the pressure of fluid delivered by said pump and also comprising a piston of larger diameter normally subjected to the relatively low pressure of fluid delivered by said supercharger acting in opposition to pressure of fluid on said small piston, and said means being responsive to an increase in the pressure of fluid acting upon said piston or small diameter above a certain normal degree to decrease the pressure of fluid delivered thereby to said certain normal degree.

11. A fluid pressure pump equipment comprising a high pressure pump variously condtionable to deliver fluid at various high pressures, a supercharger operative to deliver fluid at a relatively low pressure to said pump, means operative to condition said pump to vary the pressure of fluid delivered thereby, said means comprising a piston of small diameter and subjected at all times to the pressure of fluid delivered by said pump and also comprising a piston of larger diameter normally subjected to the relatively low pressure of fluid delivered by said supercharger acting in opposition to pressure of fluid on said small piston, and said means being responsive to an increase in the pressure of fluid acting upon said piston of small diameter above a certain degree to decrease the pressure of fluid delivered thereby to said certain degree and also being responsive to an increase in the pressure of fluid acting on said piston of larger diameter to condition said pump to operate to increase the pressure of fluid delivered thereby, and means operative to effect the flow of fluid under high pressure from said pump to said piston of larger diameter to effect the operation of the first said means.

12. A constant speed fluid pressure pump comprising in combination a rotatable portion, a bearing portion shiftable relative to said rotatable portion for varying the volume of fluid delivered by said pump, means operative to shift said bearing portion relative to said rotatable portion, said means comprising a, piston of small diameter subjected at all times to the pressure of fluid delivered by said pump and a piston of relatively larger diameter normally subjected to a relatively low degree of fluid pressure, said means being normally responsive to the pressure of fluid actin upon said piston or small diameter to shift said bearing portion in a direction to limit the volume of fluid delivered by said pump and thereby obtain a certain degree of pressure therein, and operative in response to the pressure of fluid delivered by said pump which may act upon said piston of larger diameter to shift said bearing portion to a position in which a predetermined volume of fluid may be delivered by said pump, and means operative to eifect the flow of fluid under pressure from said pump to said piston of larger diameter.

13. A fluid pressure pump equipment comprising a high pressure pump variously conditionable to deliver fluid at various high pressures, a supercharger operative to deliver fluid at a relatively low pressure to said pump, means operative to condition said pump to vary the pressure of fluid delivered thereby, said means comprising a piston of small diameter subjected at all times to the high pressure 0r fluid delivered by said pump and also comprising an opposing piston of larger diameter normally subjected to the relatively low pressure of fluid delivered by said supercharger, and said means being responsive to an increase in the pressure of fluid acting upon said piston of larger diameter to condition said pump to operate to increase the pressure of fluid delivered thereby, control means having at least two control positions and operative to one control position to effect the flow of fluid under high pressure from said pump to act upon said piston of larger diameter and operative to its other control position to out off the flow of fluid from said pump to said piston of larger diameter,- valve means operative to prevent the back flow of fluid under pressure from said piston of larger diameter to said pump, and a choked communication always open to the fluid delivery side of said supercharger through which fluid acting upon the larger piston flows and thereby effects a reduction in the pressure of fluid acting upon the larger piston when said control means is moved from its said one control position to its said other control position.

' HARRY C. MAY.

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

UNITED STATES PATENTS Number Name Date 1,563,282 Jessup Nov. 24, 1925 2,130,299 Ernst Sept. 13, 1938 2,145,547 Landenberger Jan. 31, 1939 2,214,552 Ferris Sept. 10, 1940 2,333,530 Ernst Nov. 2, 1943 2,350,662 Adams June 6, 1944 2,386,459 Hautzenroeder Oct. 9, 1945 2,388,010 Pohl Oct. 30, 1945 2,395,633 Livers Feb. 26, 1946

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