US2557345A - Liquid level responsive fluid motor system - Google Patents

Description

June 19, 1951 D. J. FRANCKI 2,557,345

LIQUID LEVEL RESPONSIVE FLUID MOTOR SYSTEM Filed Nov. 16, 1946 2 Sheets-Sheet 1 INVENTOR. Dav/v) J Fen/vex! June 19, 1951 D. J. FRANCKI 2,557,345

LIQUID LEVEL RESPONSIVE FLUID MOTOR SYSTEM Filed Nov. 16, 1946 2 Sheets-Shet 2 INVENTOR. flew/v Yd: FEM/cm Y Patented June 19, 1951 LIQUID LEVEL RESPONSIVE FLUID MOTOR SYSTEM Denny Joseph Francki, Chicago, Ill.

Application November 16, 1946, Serial No. 710,290

2 Claims.

My invention relates to a fluid motor for conversion of the energy of a body of water to useful mechanical energy.

It is an object of my invention to provide an improved fluid motor.

It is a further object of my invention to provide an improved fluid motor capable of deriving useful work from a .small flow of fluid.

Yet another object of my invention is to provide a fluid motor capable of deriving useful work from a small flow of fluid over a moderate distance.

Yet another object of my invention is to provide a fluid motor having features of construction, combination, and arrangement, wherein it is inexpensive in construction and reliable in operation to the end that it maybe utilized for a maximum number of practical operations where a fluid, such as water, is available as a source of energy.

The novel features which I believe to be characteristic of my invention are set forth with particularity in the appended claims. My invention, itself, however, both as to its organization and method of operation, together with further objects and advantages thereof, may best be understood by reference to the following description taken in connection with the accompanying drawings.

On the drawings:

Figure 1 is a somewhat diagrammatic view showing the complete fluid motor embodying the features of my invention;

Figure 2 is a more detailed somewhat diagrammatic view of portions of my invention as illustrated in Figure 1;

Figure 3 shows in detail the mechanical movement for converting the up and down motion of the pistons of my invention to useful rotary motion; and

Figures 4 and 5 show the valve actuating mechanism utilized in the embodiment of my invention illustrated in Figure 1.

As shown on the drawings:

In Figure 1, the container of liquid from which energy is derived is designated at In, liquid in this container having greater elevation, and hence greater static energy, than the liquid at the point of discharge I2. From source ll], the liquid flows through pipe 54 to inlets 2B and 29 of cylinders I6 and It, the latter being connected to cylinder l6 by pipe 29. Overflow pipe 22 provides an outlet for fluid from pipe 20 and cylinders H5 and l 8 when there is excessive pressure therein so as to prevent overloading the appara- 6!] and 62.

tus. From cylinders 16 and 18, fluid flows from outlets 352 and 31 through pipes 24 and 25 to be discharged at point I2.

7 Cylinders l6 and I8 are terminated at their lower ends by pistons 35 and 38, Figure 2, re-, spectively, each of these being connected to the corresponding cylinder by Sylphon bellows 49 and 42,, respectively. Each piston is further con:

nected to connecting rods 44 and 46 so that the downward or upward force on the pistons themselves is communicated to rods 48 and v50, Figure 1, which are pivotally mounted about shafts 52 and 54, respectively, and are pivotally connected to connecting rods 44 and 46, respectively. In

addition, the forces on pistons 36 and 38 are communicated to connecting rod 5| which is pivotally mounted on shaft 53. nections could be of the lost-motion type to facilitate the respective movements of the rods.

As will be evident from inspection of Figure 3, rods 48 and 50 are pivotally connected to pawls 55 and 58, respectively, so that motion of either of these rods in the pawl-engaging direction causes corresponding rotation of ratchet wheels Similarly, rod 5! is pivotally connected to pawl 59 so as to rotate ratchet wheel 6.! when rotated in the pawl-engaging direction. As will be described in further detail hereinafter, ratchet wheels 6!) and 62 are provided with gear teeth so as to be mutually engaged with gear 63, to the end that the angular velocities of wheels 69, 6!, and 62 are maintained constant relative to each other. Thus, as the pistons 35 and 38 execute reciprocating movement, the shaft 53 is rotated and useful mechanical work may be obtained therefrom.

Figure 2 is a cross section view showing in more detailed fashion the valve mechanism whereby pistons 35 and 38 are caused to execute reciprocating motion as a consequence of the flow of fluid through cylinders l6 and [8. .As shown in this figure, the valve mechanism is arranged for the condition wherein piston 36 is executing downward motion and piston 38 is executing upward motion. As will be evident from inspection of Figure 2, the main control of the valve mechanism is achieved through the actuating device shown generally at 6 this device being pivotally connected to a connecting rod 45 at point 66 and having its operating arm 55 pivotally connected to point 16 to operate the valve mechanism. With respect to the flow of fluid to cylinder IE, it will be observed that actuating device 64 controls two separate valves 72 and 16. The former valve controls the inlet of water or other fluid The various confrom source I to the lower portion of cylinder I6, and consists of rod 18 pivotally connected to operating arm 60, the latter being connected to pivot I0 by rod 82. Thus, as pivot is depressed, valve 12 is opened and as pivot I6 is raised, valve 12 is closed. In the closed position, valve 12 forms a seal with member I3 to prevent fluid flow to the lower portion of cylinder I6. Valve I6 is also connected to operating arm 82 so as to be closed when pivot I0 is depressed. It is thus evident that, as pivot 10 is depressed, valve I6 is closed and valve I2 opened. On the other hand, if pivot 10 is raised by corresponding motion of connecting rod 44, valve I6 is opened and valve 12 closed.

The flow of fluid through cylinder I8 is controlled by valves 86 and 90. These valves are actuated by rod 92 which is caused by lever 94 to assume a position opposite to that of rod 82. Thus, when pivot point I0 is depressed so as to close valve 16 and open valve I2, lever 94 raises rod 92 to open valve 90 and close valve 86, valve 86 being closed by reason of its connection through rod I00 to operating arm 98 and hence rod 92. Thus, as pivot point 10 executes reciprocating motion in accordance with motion of connecting rod 44, the valves 86 and 90 execute motion opposed to that of valves "I2 and I6, thereby causing periodic fiow of fluid in operating cylinders I6 and I8, the flow in cylinder I6 being 180 out of phase with that in cylinder I8.

A strainer II is provided in container I0 to prevent entrance of foreign matter into the operating mechanism of the fluid motor.

Valve I2 and 86 in open position permit air trapped in the tanks I6 and I8, respectively, to be vented. I

Downwardly extending skirts I! are provided to protect bellows 40 and 42 and prevent damage thereto. Assembly of the unit is facilitated by supports I9 which are attached at their upper ends to bellows 40 or bellows 42 and may be attached at their lower ends to skirts H, the latter attachment being achieved by support plates 2I attached to skirts H by wing nuts or similar devices (not shown).

Hand operated valves 14 and 88 are provided in pipes 24 and 26, respectively. It is the function of these valves to prevent leakage of fluid down these pipes when the fluid motor is not operating, thereby causing the motor to remain in operating condition at all times.

A tank (not shown) may be provided at the outlet valves I6 and 90 so that fluid is discharged therefrom into the fluid of the tank. This further reduces the tendency of pipes 24 and 26 to drain when the motor is not in use.

Figure 3 is an isometric view showing the connection of connecting rods 44 and 46 and wheels 60, 6| and 62 to convert the up and down reciprocating motion of pistons 36 and 38 to useful mechanical energy. As shown in this view, shaft 53 is supported by bearings I02, these bearings being positioned so that the gear teeth on wheels 60 and 62 engage corresponding teeth on wheel 63. As connecting rod 44 is forced in the downward direction by pressure exerted on piston 36, pawl 59 engages wheel 6| to cause motion of that wheel in the counterclockwise direction. Pawl 55 slips over gear 69 so no force is transferred thereto. On the upstroke of rod 44, pawl 56 engages gear 60 to cause rotation thereof in the clockwise direction and corresponding counterclockwise rotation of gear 63 and shaft 53. Pawl 59 slips under this condi tion. Similarly, as connecting rod 46 is forced in the downward direction by pressure from cylinder 38, pawl 58 engages wheel 62 and forces that wheel in the clockwise direction, thereby rotating shaft 53 through gear 63 in the counterclockwise direction. Pawl 59 slips under this condition. On the upstroke of piston 38, pawl 58 slips over wheel 62, but pawl 53 engages to rotate shaft 53 in the counterclockwise direction. If desired, the variations in angular velocity of shaft 53 associated with the periodic application of torque from pawls 56, 58 and 59 may be reduced in magnitude by a flywheel such as I06 attached to rotate with shaft 53. Of course, the device for which the mechanical energy is desired, such as a stamping machine, air pump, saw, etc., is likewise connected to shaft 53.

It will be observed that the effect of the mechanism shown in Figure 3 is positively to rotate shaft 53 in the counterclockwise direction regardless of whether rods 44 and 46 are ascending or descending.

The valve operating mechanism 64 is shown in Figure 4. It is the purpose of this mechanism to convert the continuous reciprocating motion of connecting rod 44 to actuate valves I2, I6, 86, and in accordance with the position of the pistons and thus cause continuous operation of the motor. This mechanism comprises a support I48 which is adapted to be secured in any suitable manner to the point of support of the apparatus. Operatively mounted on a pivot pin I49 is a plate I50. Plate I50 carries the arm I28 which is adapted for connection to the valve operating rod 82, Figure 2, at pivot I6 and is connected to plate I50 by bolt I52. The bolt I52 enables the arm I28 to be angularly adjusted relative to the plate I50. The plate I50 is provided at one portion of its periphery with a recessed portion I53 into which there projects a detent I54 mounted on the support I48.

Extending oppositely from the arm I28, the other arm I30 is pivoted to the support I48 by screw I59. The outer end I56 of this arm is adapted for connection to the connecting rod 44 which oscillates the arm I30 in response to the motion of the piston 36. The inner end I51 of the arm I30 forms a shoulder I58 having a curved surface of constant radius relative to the pivot pin I59 of the arm I30. The shoulder I58 forms a latch against which a projection I60 of the plate I50 abuts.

The end I51 of the arm I30 is bent to form an outwardly extending right angle portion I6I to which a leaf spring I62 is connected by means of bolt I63. The free end of the spring I62 is disposed between a pair of spaced posts I64 which are located on plate I50 opposite the inner end of the arm I28.

It will be observed that when the arm I28 is in the raised position, as shown in full lines, the detent I54 is in engagement with the right end of the recessed portion I53 of the plate I50 and the projection I69 abuts the outer surface of the shoulder I58. In this position the spring I62 is inactive and not flexed in either direction. If the arm portion I56 is now moved upwardly, as shown in the full lines of Figure 5, the shoulder tends to move outwardly to such a position as to release the engagement of the projection I60 therewith. The spring I62 is now flexed downwardly so as to cause the plate I50 to rotate in a clockwise direction with a snap action as soon as the shoulder I58 moves out of engagement with the projection I60. The plate then rotates until the detent I54 engages the left end of the recessed.

portion I53, thus moving arm I28 downwardly and operating the valves. The final position assumed is shown in the dotted lines of Figure 4. It will be noted that the spring is not flexed in this position. On the opposite stroke, the portion I56 of the arm I30 is moved: downwardly until the position shown in the dotted lines of Figure 5 is reached. In this position, the projection I66 engages the inner surface of shoulder I58 and the spring I62 is flexed as shown in the dotted lines. Upon further movement of the arm I56, the end I51 moves as shown in the dotted lines of Figure 5, until the projection I66 is released by the shoulder I58. This inward movementcauses the spring I62 to be straightened to the position shown in the solid lines in Figure 4, so that the moment the projection I60 is released the plate I50 is rotated in the counterclockwise direction until the detent I54 again engages the right end of the recessed portion I53, thereby returning the valves to their initial positions.

It will be apparent that with a valve operating mechanism as described above, the valves are opened and closed with a snap action, although the end 56 of arm I30 is oscillated with uniform motion.

Having described the construction of an illustrative embodiment of my invention and the various elements thereof, I will now outline its operation.

In executing reciprocating movement, the pistons 36 and 38 each pass through two conditions of operation: one corresponding to the downstroke of connecting rod 54 and upstroke of connecting rod 46, and the other corresponding to the reverse strokes of these rods. Referring to cylinder I6, when the downstroke is executed, valve I2 is open and valve 16 is closed. In this condition the liquid in source I6 is in communication with the liquid acting against the surface of piston 36. Thus the downward pressure on piston 36 is equal to the head of liquid corresponding to the difierence in elevation between piston 36 and the liquid level in source Ill plus the difference in the air pressure on the upper surface of the fluid in source I6 and the lower surface of the piston 36. This pressure is, of course, somewhat reduced by the friction losses incident to passage of fluid into the lower porr tion of cylinder I6. This force, which is, of course, in the downward direction, acts through connecting rod 44 to produce torque on shaft 53. On the upstroke, valve I2 is closed and valve I6 is open. In this case the fluid in cylinder I6 is in communication with the air pressure at point I2. The effective pressure exerted on piston 36 then becomes the difference between the upward pressure exerted by air pressure at the bottom of this piston and the-downward pressure due to the liquid above it. This pressure may be made to have a net upward direction by causing the level of the discharge at point I2 to be below the level of the piston. The pipe 24 then forms a syphon for the removal of water displaced by the upward movement of the piston through outlet 36. The upward force acting on the piston due to atmospheric pressure is equivalent to the pressure head of approximately 32 feet of water. As nearly this same atmospheric pressure acts at the discharge point 12, the force causing the syphon to operate is that attributable to the weight of water standing in pipe 24 between the level of the piston and the point I2. Thus, the lower the point I2, the stronger will be the syphon 6 action and the more rapid theupward movement of the piston.

If, however, the height of water standing in the cylinder above the piston exceeds 32 :feet, the piston will not rise until the excess is discharged through the outlet 30. To prevent this delay, and to restrain the pistons upward movement as little as possible, the cylinder should be made very shallow. Then, with the sealing valve I2 only a short distance above the level of outlet 36, the piston will rise quickly'a'gainst a very small head of water. Moreover, the outlet should be at as low a level with respect to the cylinder as is feasible, taking full advantage of the pressure head of water in the cylinder 'to efiect a rapid discharge.

An added advantage of a shallow cylinder is that only the Water displaced by the piston will be discharged in each cycle. When valve 12' is periodically opened, this amount will be replenished by the water under pressure from the elevated source In and the atmospheric pressure thereupon, which will displace the piston downwardly. If the outlet point I2 is not so low as to draw a vacuum, the cylinder may thus always be kept filled with water.

The operation of cylinder I8 and piston 38 is identical with that above described for cylinder I6 and piston 36.

My invention is susceptible of various modifications and alternative constructions. In particular, the device may comprise only a single cylinder which is caused to execute reciprocatory motion as described above. In this case the successive applications of torque to a single ratchet wheel will maintain that wheel in continuous rotation because of the inertia of the moving parts.

While I have shown a particular embodiment of my invention, it will, of course, be understood that I do not wish to be limited thereto since many modifications, both in the elements employed and their cooperative structure may be made without departing from the spirit and scope of my invention. I, of course, contemplate by the appended claims to cover all such modifications and alternative constructions that fall within the true spirit and scope of my invention.

I claim as my invention:

1. In combination in a fluid motor system, a fluid-tight chamber having a movable wall, an inlet and an outlet, the external face of said wall being in communication with atmospheric pressure, a container for a body of liquid at a greater elevation than said chamber and in communication With said inlet, a first valve means for closing said inlet, a pipe connection for said outlet and an orifice for the discharge thereof in elevation below the lowermost position of said movable wall, a second valve means for closing said orifice, and means actuated by movement of said movable wall to operate said first valve means to close said inlet and to operate said second valve means to open said orifice when said chamber becomes distended by static pressure of said liquid, said system including means for venting said chamber, so that said pipe connection will syphon said liquid from said chamber to reciprocate said movable wall.

2. In combination in a fluid motor system, a pair of fluid-tight chambers each having an in let and an outlet, a container for a body of liquid at a greater elevation than said chambers and in communication with each said inlet, first valve means for closing each said inlet, a pipe connection for each said outlet and each discharging through an orifice, a second valve means for closing said orifice, said chambers having a movable wall such that each chamber may be distended by static pressure of said liquid, and means actuated by said movable wall to operate said first and second valve means respectively to close the inlet and to open the orifice of the distended one of said chambers and contemporaneously to open the inlet and close the orifice of I the contracted one of said chambers, the face of said wall external to the distended one of said chambers being in communication with atmospheric pressure to alternately contract said chambers, each said orifice being lower in elevation than said movable wall, said system including means for venting said chambers, whereby liquid is syphoned from the distended one of said chambers through its associated pipe connection.

DENNY JOSEPH FRANCKI.

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

UNITED STATES PATENTS 10 Number Name Date 69,591 Sabin Oct. 8, 1867 208,291 Carr Sept. 24, 1878 286,803 Fletcher Oct. 16, 1883 333,314 Lidback Dec. 29, 1885 15 1,036,587 Doyle et a1 Aug. 27, 1912 2,000,781 Mood May 7, 1935

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