US3478645A

US3478645A - Fluid powered timing devices

Info

Publication number: US3478645A
Application number: US640988A
Authority: US
Inventors: Carlos R Canalizo
Original assignee: Otis Engineering Corp
Current assignee: Otis Engineering Corp
Priority date: 1967-05-24
Filing date: 1967-05-24
Publication date: 1969-11-18
Anticipated expiration: 1986-11-18

Description

C. R. CA NALIZO Nov. 18, 1969 FLUID POWERED TIMING DEVICES 3 Sheets-Sheet l mm .nu

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INVENTOR Carlos R. Conolzo Wd@ M FLUID POWERED TIMING DEVICES s sheets-sheet 2 Original Filed Dec. 17, 1964 INVENTOR Carlos R. Canolizo 5 ATroRNEYs 2, Nw mm. 4Q NQ W ww ortl f.\ ENQ MMT@ Je s NN in, .n E g S 4 l um mm 0.2 n@ www M w mm Nov. 18, 1969 C- R- CANAl-ZO 3,478,645

FLUID POWERED TIMING DEVICES Original Filed Dec. 17, 1964 i 3 Sheets-Sheet 3 Fig.9

INVENTOR Carlos R. Con-ollzo BY @94M United States Patent 3,478,645 FLUID POWERED TIMING DEVICES Carlos R. Caualizo, Dallas, Tex., assignor to Otis Engineering Corporation, Dallas, Tex., a corporation of Delaware Continuation of application Ser. No. 419,112, Dec. 17, 1964. This application May 24, 1967, Ser. No. 640,988 Int. Cl. F011 /14, 31/04; F01b 19/02 U.S. Cl. 91-335 4 Claims ABSTRACT OF THE DISCLOSURE A gas operated timing device having a diaphragm alternately displaceable in opposite directions by gas under pressure which is supplied alternately to opposite sides of the diaphragm through suitable control means.

This application is a continuation of application Ser. No. 419,112, filed Dec. 17, 1964, now abandoned.

This invention relates to timing devices. More specilically this invention relates to fluid actuated timing devices.

It is an object of this invention to provide a new and improved fluid actuated timing device.

It is another object of this invention to provide a tim- -ing device driven by a substantially constant supply of fluid under pressure to produce timed mechanical movement.

It is an additional object of the invention to provide a lluid actuated timing device employing a single diaphragm which is alternately displaced in opposite directions by a supply of fluid as distinguished from dual diaphragms as used in conventional uid operated timers.

It is a further object of this invention to provide a fluid actuated timing device which meters fluid ow to a diaphragm for displacing the diaphragm to produce periodic mechanical movement.

It is a `further object of the invention to provide a fluid actuated timing device in which the reciprocating action of a flexible diaphragm is translated into rotational motion.

It is a further object of the invention to provide a fluid actuated timing device in which the longitudinal motion of a rod generated by a reciprocating diaphragm is used to actuate a valve controlling a supply of metered fluid to the diaphragm.

It is a still further object of the invention to provide a fluid actuated timing device operable on a readily adjustable time cycle.

It is another object of the invention to provide a fluid actuated timing device in which the cycle of operation of the device is controllable in response to changes in the quantities of the metered uid supplied to the device.

It is an additional object of the invention to provide a fluid actuated timing device which may be employed to power clocks, recorders, and other related mechanisms including such apparatus as valves.

Additional objects and advantages of the invention will be readily apparent from the reading of the following description of a device constructed in accordance with the invention, and reference to the accompanying drawings thereof, wherein:

FIGURE 1 is a longitudinal view partially in elevation and partially in section illustrating a gas timer constructed in accordance with the invention with the valve positioned to drive the diaphragm downwardly;

FIGURE 2 is a side view in elevation of the apparatus of FIGURE 1;

FIGURE 3 is a fragmentary view in section illustrating the valve mechanism of the timer in a position to drive the diaphragm upwardly;

FIGURE 3-A is a fragmentary view partially in seclCC tionl and partially in elevation illustrating the back sides of the valve element and the cam actuating apparatus as illustrated in FIGURE 3 showing in particular the lostmotyion system used in rotating the valve actuating cam;

FIGURE 4 is a fragmentary view in elevation of the back side of the portion of the timer illustrated in FIG- URE 3;

FIGURE 5 is a view in section along the line 5 5 of FIGURE 1 illustrating the valve element and the exhaust passage therefrom;

FIGURE 6 is a view in section along the line 6--6 of FIGURE 5 illustrating only the valve element and the hollow shaft on which the element is mounted;

FIGURE 7 is an exploded view in perspective of the valve element looking at the bottom side thereof and the shaft on which the valve element is mounted;

FIGURE 8 is a view in perspective of the rack and pipion motion translation assembly employed in the timing-device; and,

FIGURE 9 is a view partially in elevation and partially in section taken along the line 9 9 of FIGURE 1.

Referring to FIGURE 1, the timer 10 generally comprises a metering valve 11, a selector valve assembly 12, a diaphragm assembly 13, and a motion translation assembly 14. Fluid undei pressure is supplied to the timer through the line 15 which connects through a pressure regulator 20 and a filter 21 to a source of gas under pressure. As shown in FIGURE 2 in which the pressure regulator and filter are removed, the motion translation aS- sembly 14 is connected through a shaft 22 to a gear assembly 23 which drives a timer Wheel 24 employed to trip a valve 25. The timer is supported on a suitable mount Btl-which may be a piece of pipe clamped to a lflow line or a post or similar type member set in cement in the ground.

Referring to FIGURE 1, the metering valve 11 includes a body 31 provided with an inlet passage 32 and an outlet passage 33 which communicate with a bore or chamber 34. A needle 35 is threadedly engaged through the body and extends into the chamber 34 to cooperate with the passage 33 to control flow through the metering valve. Themetering valve is connected to the conduit 15 by a suitable coupling 40 and a threaded connecting member 41. The metering valve is secured into the body of the selector valve 12 by a connecting member 42 through which the llow passage 33 extends to conduct uid into the selector valve from the metering valve. The connecting member 42 may be a separate part or it may be formed as an integral part of the body 31 of the metering valve.

The selector valve assembly 12 has a body 12a which also houses the motion translation assembly 14. The selector valve includes a chamber 43 and a chamber 44 formed in the body and interconnected by the ports 45 in the Wall 50 which separates the chambers within the body. As shown in FIGURE 5, the chambers are closed by a cover plate 50a secured to the valve body by screws 50h. A fluid flow passage 51 extends through the body from the chamber 44 to the exterior of the body to exhaust fluid from the chamber to the atmosphere. The valve body is also provided with

flow passages

52 and 53 which function to conduct uids between the chamber 44 and the diaphragm assembly. Each of the

flow passages

51, 52, and 53 open into the same wall of the valve body so that fluid flow between the valve chamber and the passages may be controlled by the valve element 54 which fits over the openings of the flow passages into the chamber. The valve element 54 is pivoted within the chamber 44 on the tubular shaft-conduit 54a so that it may rotate between the positions illustrated in FIGURES 1 and 3 to selectively cover and uncover the openings of the passageways. The details of the valve element and its mounting are shown in FIGURES 5, 6 and 7.

Referring specifically to FIGURES 5, 6 and 7 the valve element 54 is preferably molded from a suitable material such as Teflon with a cavity 54b formed therein. The cavity serves to conduct the fluids through the valve element between the several passages covered by the element at its different positions. The central portion of the valve element of 54C is molded to the configuration illustrated so that the hollow shaft 54a will t in rotational relationship within the valve element without the necessity of using further securing means between the element and the shaft. As best seen in FIGURE the shaft 54a extends only partially into the valve element so that the fluid flow may occur from the cavity 5417 into the open end of the shaft 54a within the cavity. The shaft 54a is secured into the flow passage 51, as seen in FIGURE 5. Since the valve element functions to selectively connect the

passages

52 and 53 to the exhaust passage 51 it is necessary that fluid flow occur through the Valve element cavity into the hollow shaft. The bore 54d of the hollow shaft thus serves as an outlet from the cavity of the valve element. The protrusion 54e on the top of the valve element rests against the inner surface of the cover plate 50a to hold the valve element on the hollow shaft over the passageway openings. Exhaust fluid flowing into the passage 53a moves through the cavity 54h of the valve element into the open end of the hollow shaft, through the bore 54d, and out of the body of the valve through the passage 51 to the atmosphere. The pressure of the fluid within the chamber 44 over the valve element holds the valve element against the back face of the chamber with sufficient tightness to prevent leakage of the exhaust fluids flowing through the valve element.

The valve element 54 is rotated between the two illustrated positions by a cam 55 which is loosely supported on a shaft 60 extending through a Wall of the body of the valve. Referring to FIGURES 1 and 3, the cam S5 is provided with an edge 55a joining the concave corner 55b and an edge 55e joining the other concave corner 55d. The rotate the valve element from the position illustrated in FIGURE 1 to the position illustrated in FIG- URE 3 the cam 55 is rotated counter clockwise with the edge 55a engaging the lower end of the Valve element to shift the valve element in a counterclockwise direction to the position shown in FIGURE 3. The cam is rotated in a clockwise direction to return the valve element to the position illustrated in FIGURE 1 with the edge 55e engaging the upper end of the valve element to displace the valve element clockwise back to the position shown in FIGURE 1. Referring to FIGURE l, any force which might urge the valve element in a counterclockwise direction will cause the upper end of the element to engage the concave 55d effectings a locking relationship between the cam and the valve element so that the cam will retain the valve element in the position shown. The same relationship will exist between the concave lower corner 55d and the lower end of the valve element when the relative positions of the members are as illustrated in FIGURE 3. Referring to FIGURE 3-A, a peripheral flange 56 is formed on and extends around a portion of the back side of the cam 55 to provide a surface against which a force may be applied to rotate the cam. A driving member 57 is rigidly secured on the shaft 60 adjacent to the back side of the cam within the flange 56 so that the driving member may engage the flange to move the cam between the two valve positions necessary for operation of the timer. The two limits of rotational movement of the driving member are illustrated in FIGURE 3-A by the solid and dotted line representations of the member. When the cam is to be moved upwardly from the position illustrated in FIGURE 3-A the driving member is moved by the shaft 60 to the position represented by the dotted lines at which position the driving member engages the inside of the flange 57 to turn the cam in an upward direction. A lost-motion relationship exist between the driving member 57 and the cam. Such a lost-motion relation- 4 ship is necessary in order for the snap action assembly, which will be explained hereinafter, to abruptly shift the positions of the cam and valve element. A rod 61 is connected as one end to the cam 55 by a pin 62. A slot 63 is formed in the other end of the rod 61 to accomodate a pin 64 secured into the valve body. A washer 65 is fitted around the rod 61 near the end adjacent to the cam 55. The pins 66 and 67 are secured into the valve body to limit the travel path of the washer 65 as it moves the cam between the two positions required. A spring 70 is engaged around the rod between the pin 64 and the washer. A spring 70` is engaged around the rod between the pin 64 and the washer. The spring and arm assembly connected to the cam provide a snap-action in the cam causing the cam to snap or move abruptly from one position to another once the cam passes a deadcenter position. Such a dead center position exists when the pin 62 passes a line connecting the center of the pin 64 and center of the shaft 60. The snap-action of the cam is made possible due to the lost-motion relationship between the cam and the driving member 57, as previously mentioned. The driving member is rotated by the shaft 60 with the driving member engaging the flange 56 and moving the cam 55 to the dead-center position at which point the snap-action assembly takes over with the spring pressing the washer against the cam to abruptly snap the cam to the next position. For example, in moving the cam from the position illustrated in FIGURE 3-A the shaft 60 will rotate the driving member 57 to the position illustrated by the dotted lines so that the driving member will engage the cam and lift the cam and spring mechanism upwardly until the dead-center position is reached at which location the spring acting through the washer will abruptly shift the cam to an upward position with the washer travel path being stopped when it engages the pin `67. The lost-motion relationship of the cam on the shaft permits the spring and washer to freely and quickly snap the cam to this second position as there is the freedom of motion between the driving member and the cam illustrated is FIGURE 3-A so that the cam is free to be abruptly shifted a sufficient distance to actuate the valve element. If the cam were rigidly fixed on the shaft 60 the abrupt movement of the cam would not be possible inasmuch as the other end of the shaft 60', as will be explained hereinafter, remains at all times securely connected to the motion translation assembly. The shaft 60 on which the cam is mounted is interconnected with the motion translation apparatus 14 in a manner which will be explained.

The diaphragm assembly 13 includes a housing 71 which is secured on the body 12a around the boss 12C by a plurality of screws 72. The bottom of the body 12a is provided with a groove 73 in which is fitted a ring seal 74 to effect a fluid tight seal between the body and the diaphragm assembly housing. The diaphragm assembly housing is divided into two substantially equal chambers or compartments 75 and 80 by a flexible diaphragm 81. The chamber is interconnected with the chamber 44 in the selector valve 21 through the flow passage 53. A conduit 82 is connected between the selector valve and the chamber 75 by

suitable fittings

83 and 84, respectively.

The fitting 83 is engaged in the bore 83a of the body to provide fluid communication between the conduit and the passage 52 whereby fluid may flow between the selector Valve and the chamber 75 through the conduit 82.

A substantial area around the center of the diaphragm s confined between the plates and 91 which are secured on a shaft 92 by a nut 93. The shaft 92 is fitted through and supported by the bearing member 94 which is locked in the body 12a by a lock ring 95. Leakage between the bearing member and the body is prevented by a ring seal while leakage between the shaft 92 and the bearing member is prevented by a ring seal 101.

The outward end of the shaft 92, as best seen in FIG- URE 8, is bifurcated to form the

parallel arms

102 and 103 which are provided withracks 10211 and 103a. The racks mesh with the pinions 104 on the shaft 22 to rotate the shaft. The racks are displaced from each other in planes parallel to the view of FIGURE 1 a minimum distance to allow a pinion on the shaft 22 to mesh with only one of the racks. In the embodiment illustrated the shaft is provided with two pinions, one to mesh with each of the racks. The pinions are supported on the shaft and are operatively connected thereto by suitable spring clutch connections whereby the shaft is rotated in a single direction by the pinions which are actuated by the racks 102:1 and 103a as the racks reciprocate in response to moment of the diaphragm. Referring particularly to FIG- URES 8 and 9, the pinions 104 are engaged with the shaft 22 through the spring clutch assemblies 104a which provide single direction rotational motion to the shaft'tfrom the pinions. Each of the clutches 104a includes hub 104b which is secured to the shaft 22 by a set screw 104C. The hub is reduced in diameter along a section 104d which forms a sufficiently loose fit in the pinion that the pinion may rotate around the hub when not driving the hub. The pinion is engaged on the hub and locked thereto by a locking ring 104e. The llange 104i of the pinion extends from the body of the pinion over the hub, as illustrated in FIGURE 9. A tightly wound coil spring 104g is disposed around the hub 104b and the flange 104)c of the pinion. The coil spring serves to interconnect the pinion and the hub so that the hub may be driven by the pinion to rotate the shaft. When the pinion is rotated in a direction which tends to more tightly coil the spring the spring grips both the flange 104f and the hub 104b establishing a rigid connection between the pinion and hub to drive the shaft. When the pinion is rotated in a direction which tends to uncoil the spring, the spring ceases to serve as a linkage between the pinion and hub thus permitting the pinion to free-wheel around the hub. For example, in FIGURE 9 when the pinion in the upper portion of the ligure is rotated such that the left side of the pinion moves toward the observer, the spring will tend to be coiled tighter and thus will engage the hub to rotate the hub and the shaft. If the pinion is rotated by the rack in a direction such that the right side of the pinion moves toward the observer there is a tendency to uncoil the spring resulting in disengagement of the pinion from the hub such that the pinion will free-wheel around the hub. The coils of the springs on each of the clutches are so oriented that rotation of the pinions by the racks will cause the shaft to move constantly in a single direction. For example, looking at FIGURE 8, if it is desired that the shaft 22 rotate in a clockwise direction the coil spring on the clutch associated with the pinion on the right side of the assembly will be such that the spring will tighten as the arm 103 raises to rotate the pinion and shaft in a clockwise direction. Then, as the rack 102a is lowered on the next cycle the left-hand pinion is rotated clockwise and the coil spring on the clutch associated with the left-hand pinion is so arranged that it will tighten to also effect clockwise rotation of the shaft. As the rod 92 is raised, the rack 103a rotates the pinion associated therewith to effect the clockwise rotation of the shaft while simultaneously the pinion meshing with the rack 102a is moving freely around its respective hub. When the rod moves downwardly the rack 102a rotates its respective pinion to effect clockwise rotation of the shaft while the pinion associated with the rack 103a is now free-wheeling. A guide member 105 is secured through the body 12a into a groove 110 formed along the outer surface of the bifurcated member 102 to maintain alignment of the rod and the rack members as the rod is reciprocated by the diaphragm.

Referring to FIGURE 4, the selector valve 12 is actuated through an inter-connection between the shaft 60 and the arm 103 of the rod 92. A plate 111 is secured to the arm 103 of the rod 92 by the

screws

112 and 113. The plate is provided with a slot 114 for receiving a pin 115 secured in an arm 120. The arm 120 is held on the shaft in FIGURE l. The shaft 2.2 is connected by a suitable coupling 133 to another shaft 134 which is supported in a bearing 135. The pinion gear 140 is secured on the end of the shaft 134 and drives the

gears

141, 142 and 143. The gear 143 is supportd on a shaft 144 to which is secured the timer wheel 24. The timer wheel is provided with a plurality of clips 145 which trip the valve 25 to control fluid flow through the conduit 150. The valve 25 and shaft 44 are supported on a plate 151 which is secured to the body 12a by bolts 152, 153 and 154.

In operation, the timer 10 is connected to a source of fluid supply through the conduit 15 and the pressure regulator and filter, as illustrated in FIGURE 1. The needle 35 is adjusted to the desired iluid llow rate through the passages 32 and 33 into the chamber 43 of the selector valve. The rate of the fluid supply to the timer .determines how rapidly the diaphragm 81 will be reciprocated. The fluid flows from the chamber 43 through the ports 45 into the chamber `44. With the valve elements of the selector valve positioned, as illustrated in FIGURE 1, the valve element 54 covers the openings of the

passages

51 and 53 into the chamber leaving the passage 52 in communication with the chambetr 44. The supply fluid, therefore, flows from the chamber 44 into the passage 52, through the conduit 82, and into the chamber 75 below the diaphragm `81. The pressure of the fluid within the chamber 75 below the diaphragm forces the diaphragm in an upward direction. Since the valve element 54 is positioned over the openings of the

flow passages

51 and 53 into the chamber 55, any fluid which may be within the chamber above the diaphragm is exhausted from the chamber through the flow passage 53. The exhausted fluid flows through the cavity 54b of the valve element into the bore 54d of the shaft 54a and into the flow passage 51 which conducts it through the body of the selector valve to exhaust it to the atmosphere.

Upward movement of the diaphragm forces the rod 92 in an upward direction causing the

arms

102 and 103 the rotate the pinions 104 through the racks 102a and 103a. The rotational movement of the pinions gears is transmitted through the clutches 104a to the shaft 22 t0 rotate the shaft in one direction. As previously discussed the pinions 104 act through the springs 104g to engage the shaft which is turned each time a pinion tightens a spring. The clutches 104a are so arranged on the shaft that constant single direction motion is imparted to the shaft. The shaft 22 through the coupling 133 drives the shaft 134 which rotates the gear assembly 23. The shaft 144 is driven by the gear assembly to rotate the timer wheel 24 which, in the particular embodiment illustrated, is engageable with the valve 25 through the clips 145 which are secured around the timer wheel. The valve 25 represents a motor valve which is tripped by each of the clips on the timer wheel to permit gas pressure to escape from the valve. When each clip has passed the valve 25, the valve will close and permit gas flowing through the conduit 150 to repressure the motor valve. Thus, the clips on the timer wheel control the opening and closing of a motor valve.

Referring to FIGURE 4, as the arm 103 on the rod 92 is pushed upwardly by the perssure of the gas in the chamber 75 below the diaphragm, the plate 111 moves the pin engaged in the slot 114. As the pin 115 is carried upwardly with the rod, the arm is rotated in a clockwise direction, as viewed in FIGURE 4, effect- 7 ing clockwise rotation of the shaft 60. FIGURE 3-A is aback view of the valve oriented the same as FIG- URE 4 with the arm 120 and its associated mechanism along with the back side of the valve cover being removed to illustrate the driving member 57 of the cam. As the shaft 60 is rotated clockwise by the upward movement of the pin 115, the driving member 57, which is securely attached to the shaft 60, moves clockwise with the shaft within the flanged portion of the cam 55 with the lower edge of the driving member engaging the bottom portion of the cam flange to cause the cam to turn clockwise. The relationship of the driving member and the cam may be understood from FIGURE 3-A. The driving member engages the cam flange and turns the cam until the cam passes the dead center position at which time the snap-action assembly, including the spring and the washer, will quickly rotate the cam to the position illustrated in FIGURE 3-A. Since the cam moves freely on the shaft v60 the snap-action assembly causes the cam to rotate to the illustrated position leaving the driving member 57 in the position illustrated by the dotted lines in FIGURE 3-A. As previously mentioned, the lost-motion relationship between the driving member 57 and the cam 55 permits the snap-action assembly to rotate the cam beyond the point of rotation of the driving member and only because of this relationship may the cam abruptly snap between positions. Due to the peculiar configuration of both the valve element 54 and the cam 55, the cam does not engage the valve element until the cam is substantially at the center position which means that when the cam actually engages the valve element it is leaving dead-center position and rapidly moving so as to abruptly shift the valve element to the next position in the cycle. There is a slight amount of free-play between the cam and the valve element so that the cam may move to this dead-center position before shifting the position of the valve element. FIGURE 4 illustrates the rod at the upward end of a stroke and thus shows the arm 120 at the end of a clockwise travel path. Since the cam 55, as shown in FIG- `URES 1 and 3, is secured to the end of the shaft `60 opposite the arm 120, rotation of the shaft by upward movement of the arm 92 causes rotation of the cam 55 within the chamber 44 of the selector valve. Referring to FIGURE 3, and assuming the rotation of the shaft to the position illustrated in FIGURE 4, the cam 55 has been moved to its lowermost position. The cam has been rotated counterclockwise, as viewed in FIGURE 3, to the end of its travel path. The position of the arm 120 on the shaft 60 and the various other linkages involved in the movement of the selector valve are adjusted so that when the rod 92 is at the upper end of its travel path the valve element 54 will be shifted from the position illustrated in FIGURE 1 to the position illustrated in FIGURE 3. As the exible diaphragm 81 moves upwardly with the valve element 54 in the position illustrated in FIGURE 1, the fluid within the chamber 80 above the diaphragm is discharged from the chamber through the flow passage 53, the valve element 54, and the flow passage S1 to the atmosphere. When the diaphragm has been displaced upwardly to the farthest extent, the chamber 80 is substantially exhausted of fluid and the valve element 54 snaps from the position illustrated in FIGURE 1 to the position illustrated in FIGURE 3, in accordance with the above described procedure. As shown in FIGURE 3, flow passage 53 is uncovered by the valve element so that the supply of gas entering the selector valve from the conduit may ow through the ilow passage 53 into the chamber 80 above the diaphgram to displace the diaphragm downwardly. The valve element 54 is covering the openings of the passages S1 and 52 thereby permitting the' fluid between being exhausted from the chamber 75 to flow through the conduit 82 and subsequently be exhausted to the atmosphere through the ow passage 52, the valve element 54, and the flow passage 51.

As the diaphragm is displaced downwardly by the fluid within the chamber 80, the uid within the chamber 75 below the diaphragm is exhausted to the atmosphere through the previously described path. Downward movement of the diaphragm pulls the rod 92 downwardly causing the racks 102a and 103:1 to continue the rotation of the pinions to turn the shaft 22.. Due to the spring loaded clutch connections between the pinions and the shaft the rotation of the shaft is the same both when the racks are moving upwardly and when the racks are moving downwardly. As the member 103 of the rod 92 moves downwardly, the plate 111 carries the pin in a downward direction causing the arm 120 to rotate the shaft 60 in a counterclockwise direction. This rotation of the shaft 60, as viewed in the FIG- URES 1 and 3, will be clockwise resulting in the movement of the cam 55 from the position illustrated in FIG- URE 3 back to the position illustrated in FIGURE 1. When the cam passes dead-center it will again snap to the position illustrated in FIGURE l causing the valve element 54 to abruptly move from the position illustrated in FIGURE 3 to the position illustrated in FIGURE 1. During the downward movement of the diaphragm the fluid within the chamber 75 will have been exhausted to the atmosphere so that the chamber will again be substantially empty and ready to receive the supply uid. The previously described cycles will repeat themselves with the diaphragm continuing reciprocation to cause rotation of the shaft 22 effecting steady movement of the timer wheel 24 at a rate dependent upon the rate at which supply fluid is admitted to the' timer through the valve 11.

It will thus be seen that there has been described and illustrated a new and improved uid actuated timing device.

It will be further seen that the timing device of the invention meters fluid flow to a single diaphragm for displacing the diaphragm to produce regular mechanical movement.

It will also be seen that the single diaphragm of the timing device is alternately displaced in opposite directions by a supply of metered fluid as distinguished from dual diaphragms used in conventional uid actuated timers.

It will be additionally seen that the timing device of the invention includes a mechanism for translating the reciprocating action of a flexible diaphragm into rotational motion.

It will be further seen that the fluid actuated timing device generates longitudinal motion which actuates a valve controlling a supply of metered fluid to chambers on opposite sides of the diaphragm.

It will also be seen that the fluid actuated timing device is provided With means for readily adjusting the time cycle of the device.

It will additionally be seen that the fluid actuated timing device operates through a cycle which is controllable in response to changes in quantity of metered fluid which is supplied to the device through an adjustable metering valve.

It will also be seen that the fluid actuated timing device of the invention may be employed to power clocks, recorders, and such other apparatus as valves.

While the supply of fluid to the timing device has been described as being delivered through the adjustable valve 11, it is to be understood that the valve may be replaced with a fixed orifice which will deliver fluid to the timing device at a steady predetermined rate. If a fixed orice is to be employed in place of the adjustable valve 11 the orifice is substituted in the line 15 for the adjustable valve. Also, a fixed orice arrangement may be positioned downstream of the selector valve 12 in which event it will be necessary to employ an orifice in each 9 of the

supply lines

82 and 53 leading to each of the chambers on the opposite sides of the flexible diaphragm 81.

What is claimed and desired to be secured by Letters Patent is:

1. A fluid actuated timer comprising: a housing hava flexible diaphragm movable therein dividing said housing into two separate chambers; conduit means for conducting operating fluid to each of said chambers separately; valve means connected in said conduit means for controlling the flow of uids through said conduit means to said chambers, said valve means alternately directing fluid under pressure into one of said chambers and exhausting fluid under pressure from the other of said chambers to move said diaphragm alternately in opposite directions in said housing by means of said operating fuid; means operatively connected with said diaphragm and movable thereby for actuating said valve means in response to movements of said diaphragm to alternate the supply of fluid to one of said chambers and the exhaust of fluid from the other of said chambers; pressure control means for controlling the pressure of the uid flowing through the conduit means to the chambers to provide a desired constant operating fluid pressure supply to said chambers and orifice control means for controlling the effective orifice of said conduit means through which said fluid flows into said chambers for controlling the rate of flow through said conduit means to said chambers to provide a desired constant volume of operating fluid flow therethrough to said chambers at said constant fluid pressure to provide a constant rate of flow of operating fluid to said chambers to control the rate of movement of said diaphragm to a desired constant uniform rate in each direction; and means operatively connected with said diaphragm for translating reciprocating movement of said diaphragm to rotational motion for rotating a timing shaft unidirectionally at a constant uniform rate.

2. A fluid actuated timer comprising: a housing, a flexible diaphragm movably secured Within said housing dividing said housing into first and second chambers; a conduit connected to said first chamber for supplying uid tional movement imposed on said shaft by said motion translating assembly.

to and exhausting uid from said chambers; a conduit connected to said second chamber for supplying uid to and exhausting fluid from said chamber; a valve cOnnected to said conduits to said chambers for selectively controlling fluid flow to said chambers and having an eX- hanst uid conduit selectively connectable by said valve to said conduits to said chambers; a supply conduit for providing a supply of operating fluid to said valve for direction thereby alternately to said chambers of said housing for reciprocably moving said diaphragm alternately in opposite directions therein by means of said operating uid; fluid metering apparatus comprising a pressure regulator and an orifice control means associated with said supply conduit upstream of said valve for controlling the fluid flow rate to said chambers; said pressure regulator providing a desired constant operating fluid pressure supply to said chambers and said orifice control means providing a desired orifice in said supply conduit coacting with regulator to provide a desired constant volume of flow of operating fluid therethrough t0 said chambers at said constant pressure to produce a desired constant rate of movement of said diaphragm in said chambers; a motion translating assembly connected to said diaphragm for translating the reciprocating motion of said diaphragm to a desired constant uniform unidirectional rotatonal motion of a shaft operatively connected therewith; and a linking assembly between said motion translating assembly and said valve for actuating said valve in accordance with the movement of said translating assembly to control the flow of fluid to and the exhaust of fluid from said chambers, said fluid metering means controlling the rate of reciprocating movement 0f said diaphragm to control the rate of unidirectional rota- 3. A fluid actuated timer of the character set forth in claim 2, wherein the orifice control means comprises: a variable orifice valve upstream of said valve means for -varying the desired constant volume of flow therethrough to provide a desired constant rate of flow of operating l-fiuid to the chambers of the housing providing for varying the rate of movement of the diaphragm to a desired constant uniform rate.

4L A fluid actuated timer comprising in combination:

second chamber; means providing a first conduit to said first chamber; means providing a second conduit to said second chamber; a supply conduit for operating fluid; a Vmultiple position valve secured to said supply conduit and to said first and second conduits leading to said chambers, said valve being provided with a fluid supply flow passage for conducting fluid from said supply conduit to said first and second conduits and having an exhaust passage; said valve when in a first position supplying uid from said supply conduit through said first conduit to said first chamber and exhausting fluid through said second conduit from the second chamber for moving said diaphragm in said housing toward said second chamber by means of said operating fluid, and when in a second position supplying fiuid from said supply conduit through said second conduit to said second chamber while exhausting fluid through said first conduit from the first chamber for moving said diaphragm in said housing toward said first chamber by means of said operating fluid; a metering orifice means and a .pressure regulator in said supply conduit upstream of said valve for controlling the fluid flow rate to said multiple position valve and therefrom to the chambers in said housing for controlling the reciprocating movement of the flexible diaphragm in said housing; said pressure regulator providing a desired constan't operating fluid pressure through said valve to said chambers and said metering orifice means coacting with said regulator to provide a desired constant volume of flow of operating fluid atsaid constant pressure through said valve to said chambers to produce a desired constant uniform rate of movement of said diaphragm in said housing; a rod extending through a wall of said housing and connected at one end of said flexible diaphragm for reciprocating longitudinal movement thereby; a motion translating assembly operatively connected with the other end of said rod for transforming the reciprocating action of said rod into a desired constant uniform unidirectional rotating motion in response to said constant uniform rate of reciprocating movement of said diaphragm; and a linking assembly connected between said motion translating assembly and said multiple position valve for actuating said valve between said first and second positions in response t0 the reciprocating action of said rod for supplying fluid alternately to said first and second chambers in said housing for moving said diaphragm reciprocably in said housing.

References Cited UITED STATES PATENTS 2,621,634 12/1952 Carey 91-347 2,907,550 10/ 1959 Heinish 91-347 2,928,423 3/ 1960 Rockwell 91--468 2,935,050 5/1960 Moulton et al. 91-347 3,064,628 11/ 1962 Canalizo et a1. 91-347 3,166,988 1/ 1965 Kohler 94-347 2,769,298 11/ 1956 Jones 91-347 PAUL E. MASLOUSKY, Primary Examiner U.S. Cl. X.R.

P04050 UNITED STATES PATENT OFFICE 569 CERTIFICATE 0F CORRECTION Patent No. 3.478.645 Dated NQYember 18. 1969 Inventor(s) Carlos R. Canalizo It is certified that error appears in the above-identified patent and that said Letters Patent are hereby corrected as shown below:

Col 3, line 39, for "The" read To Col 4, line 4, for "as" read -at- Col 4,

lines

12 and 13, delete sentence beginning "A spring 70" Col 4, line 59, for "2l" read l2 Col 6, line 49, for "the" (first occurrence) read -to- Col 6, line 50, for "pinions" read pinion Col 7, line 74, cancel "between" Col. 9, lines 73-75 and Col. l0 lines 1-2 cancel "said fluid metering means controlling the rate of reciprocating movement of said diaphragm to control the rate of unidirectional rotational movement imposed on said shaft by said motion trans latng assembly" SIGNED AND SEALED JUN 2 3 1970 EAL) Attest:

Edward M. Fletcher, Ir.

nesting ofcer WILLIAM E. scum. JR.

Commissionex` of' Patents