US2646753A - Rotary fluid motor or pump having axially sliding vanes - Google Patents

Description

July ,28, 1953 c. M. ZOLL 2,646,753

ROTARY FLUID MOTOR 0R PUMP HAVING AXIALLY SLIDING VANES 4 Sheets-Sheet 1 Original Filed March 15, 1945 C. M. ZOLL July 28, 1953.

ROTARY FLUID MOTOR OR PUMP HAVING AXIALLY SLIDING VANES Original Filed March 13, 1945 4 Sheets-Sheet 2 July 28, 1953 c. M. zou. 2,646,753

ROTARY FLUID MOTOR 0R PUMP HAVING AXIALLY SLIDING VANES Original Filed March 13, 1945 4 Sheets-Sheet 5 Q N W IlHlll c. M. ZOLL 2,646,753

ROTARY FLUID MOTOR OR PUMP HAVING AXIALLY SLIDING W NES July 28, 1953 4- Sheets=-Sheet 4 Original Filed March 13, 1945 INVENTOR 611%. 2021 61 Mm ATTORNEY v Patented July 28, 1953 3 ROTARY FLUID MOTOR OR PUMP HAVING AXIALLY SLIDING VANES Carl M. Zoll, New Orleans, La., assignor to Hydro Power, Inc., New Orleans, La.

Substituted for abandoned application SerialNo.

582,452, March 13, 1945. This application February 14, 1951, Serial No. 210,889

3 Claims. (Cl. 103139) This invention .relates to rotary power devices and has special reference to a motor mechanism. The present application being a substitute for applicants abandoned application Serial No. 582,542 filed March 13, 1945.

One important object of the invention is to provide a device of this class wherein a series of pressure receiving blades are moved into and out of pressure receiving positions by a pair of cams acting positively on opposite edges of the blades.

A second important object of the invention is to provide a device wherein the cams act as abutments to form, with the blades, pressure pockets alternately arranged with exhaust pockets.

A third important object of the invention is to provide a device of this character wherein the contact of the blades with the cams is evenly maintained by spring pressed members forming elements of said blades.

A fourth important object of the invention is to provide means whereby fluid under pressure may be evenly distributed to the pressure pockets of such a device.

A fifth important object of the invention is to provide means whereby fluid may be exhausted from the exhaust pockets with a minimum of back pressure.

A sixth important object of the invention is to provide a novel device of this character having a rotor reversible in the direction of rotation.

A seventh important object of the invention is to provide a novel device of this character which may be used either as motor means or pumping means. An eighth important object of the invention isto provide a novel device of this kind which may be connected to other devices of like character to form a power transmission system.

A ninth important object of the invention is to provide a novel device of this character wherein the number of power receiving blades will exceed the number of points on the cams constituting abutment points.

A' tenth important object of the invention is to provide a novel complete power plant for this power device.

With the above and other objects in view, as will be hereinafter apparent, the invention consists in general of certain novel details of con.- struction and combinations of parts presently specifically described, illustrated in the accompanying drawings and particularly claimed.

Inthe accompanying drawings like characters of reference indicate like parts in the several views, and:

Fig. l is a side view of one form of the rotary power device as constructed in accordance with this invention.

Fig. 2 is an end view thereof.

Fig. 3 is an inside face view of one of the cover plates used with this form and disclosing the manifolds used for supply and exhaust of fluid under pressure.

Fig. 4 is a view of this form showing a face view with a cover plate and a cam plate removed.

Fig. 5 is a section on the line 5--5 of Fig. 4.

Fig. 6 is a face view of one of the cam plates used in this form.

Fig. 7 is an edge view of one cam and one cover plate in assembled relation.

Fig. 8 is a fragmentary section on the line 88 of Fig. 6..

, Fig. 9 is a fragmentary section on the line 9-9 of Fig. 6.

Fig. 10 is an end view of the modified blade.

Fig. 11 is a developed view illustrating the cam plates, blade carrier, blades and other parts in diagrammatic relation.

Fig. 12 is an assembly view of one form of power plant employing this power device.

It is first to be understood that this power device is operable with any fluid under pressure whether expansible as steam or air or incompressible as a liquid such as water or oil.

In the construction illustrated in Figs. 1 to 9 inclusive, there is provided a base member I9 adapted to rest on and be secured to any suitable foundation such as a floor or other solid object. This base member has secured thereto a heavy ring I l forming a stator. Centrally of this ring is ashaft I2 and to this shaft is fixed a rotor I3 provided with a series of equally spaced slots I4 the sides of which are radial to the center of the shaft 12. The outer ends of these slots are closed by an annular band I5 which fits closely in the ring ll. At that portion of the rotor wherein the slots [4 are formed the rotor is provided with an annular groove I6 for purposes which will be presently understood.

On each side of the ring H is mounted a cam plate or disk 11. On each of these cam plates or disks is formed a circular cam I8 which has alternate high points I9 and low points 20. The radial width of these cams is such as to cause the cams to fit closely between the bottoms of the slots 14 and the slot closing annulus l5. The high points of one cam are arranged opposite the low points of the other cam and the distance between all points on the working faces of these cams on lines parallel to the axis of the shaft l2 3 are equal in the present showing wherein the working surfaces are transversely flat.

'Slidable laterally through the slots I4 are pressure receiving blades indicated in general at 2|. The width of these blades is such that their side edges constantly engage the working faces of the earns, the width of each blade being equal to the distance between the working faces of the cams.

While the cams have been here illustrated as having their working surfaces generated by the movement of a straight line parallel to the axis of the shaft !2 on a continuous sinuous circular path and the cam engaging edges of the blades are similarly straight it is to be clearly under stood that the cams maybe otherwise shaped transversely as to their working faces, the side edges of the blades being, of course, shaped to conform thereto. For instance, the cam working faces may be transversely concave and the blades corresponding convex as to their cam engagin side edges. Under these last conditions the use of packing strips on the engaged edges of the blades may be. found advisable.

However, it is not deemed necessary to show all possible variations in the contacting surfaces of the cams and blades but one of the blade forms is shown in Fig. 10.

In the form shown in Fig. each blade has a body 24 slotted, at opposite edges as at 25 and having holes 26 extending. between these slots. In the slots 25 are fitted cam contact strips 21. Urging these strips into contact with the cams are springs 28 held in the holes 26.

Against the outer face of each of the cam plates I1 is fitted a head or cover plate 29. The ring ll, cam plates 17, and cover plates 29 are secured together by screws 30. Also each cover plate is secured to the corresponding cam plate by screws 3|. On each cover plate is a centrally disposed bearing for the shaft [2 and one of these bearings is provided with a stufiing box 32 while the other bearing may be provided with a similar stuffing box or with a cap 33 as occasion may require.

On the side of each cover plate 29 which faces the cam plate H there is provided a pair of annular concentric. channels 34 into which open pipes 35. Depending on the desired direction of revolution of the rotor one of these channels constitutes an intake or supply manifold while the other constitutes an exhaust manifold. Where the intent is that the device shall be reversible in direction of rotation a suitable valve arrangement, later to be described, enables the operator to cause the proper pipe 35 to act as'the supply pipe in accordance with the desired direction of rotation. When the device is to be used without reversal it is preferred that the exhaust passages and pipe shall be considerably larger in cross-section than the supply means so as to eliminate to a great extent any back pressure effects.

Spaced on each side of each high point 19 of a cam is port means such as is shown at 38 where each port means is formed by a plurality of bores of which one set opens into one of the manifolds 34 while the adjacent set opens into the other manifold 34. Obviously the nature and shape of such port means may vary in accordance with the size and design of the device so that applicant is not to be restricted to the exact port means here shown.

Fig. 11 shows diagrammatically the action of the device and in order to make this clear it from a tank 62 through a pipe 63.

will be noted that the supply and exhaust manifolds have been laterally displaced relative to each other, the supply manifolds being here shown at 34a and the exhaust manifolds at 34b. Also this diagram shows pressure chambers 38, exhaust chambers 39 and, under certain designs of construction certain chambers 48 will exist during certain phases of the operation which are neutral chambers since the fiuid therein is neither being exhausted nor added to. It will now be observed that since, in this diagram, all the chambers 38 are closed at their right ends by the. blades and the chambers 39 are closed at their left ends by blades the efiective fluid pressure against these blades causes the rotor to move in the direction of the arrow shown thereon.

Furthermore it will be noted that each cam has six high points while the rotor carries nine blades. Thus each blade, in one revolution of the rotor receives six impulses per side so that the total number of impulses given the rotor durin one revolution is nine times six times two or one hundred and eight. The numbers six and nine as given above are merely intended as an example but these numbers will vary greatly in accordance with the size, power and type of construction used to meet a given condition of use.

It is to be noted that the arrangement disclosed is such that while the number of blades is greater than the number of high points on one of the earns, the number of blades is not an even multiple of such number of high points so that these numbers are aliquant. This ishighly important to effect smooth running since the rotation of the rotor is caused by the action of an incompressible liquid and thus cannot depend on expansion of the driving medium as occurs in steam engines or other engines driven by a compressiblemedium or other medium expanding within the engine.

In Fig. 12 there is disclosed a complete power plant for the use of this power device. Here there is shown a motor 68 which drives'a rotary pump 6 I. This pump is supplied with oil or other liquid From the pump leads a delivery pipe 84 which is connected to a by-pass E5 controlled by a pressure regulating valve 56 so that if the pressure of the fluid to be delivered by the pipe 54- exceeds the setting of the valve (it the excess will be relieved byfi-uid returning-to the tank. The pipe 84 leads to a control valve 61. From this valve 6'! leads a pair of pipes 68 and which are branched and connected to the manifolds 34, 49 and 5| of a power device-A of the forms previously described. When the valve 5! is turned in oneposition the pipe 68 is the supply pipe and the pipe 69- the exhaust pipe but when the valve is turned in another position the pipe lid-becomes the supply and the pipe 58 the exhaust; Ihe valve 6? is connected to the tank 62 by a pipe Ill. Each of the pipes 68 and 69 is connected to a relief valve TH set preferably at 15 pounds more than the setting of the valve 66. These valves '1 l are connected to the exhaust pipe 'H by piping l2. Ihese valves are necessary in any case wherein the device A is operated by liquid and subject to sudden reversals because the inertia of the revolving rotor will-not permit its instantaneous reversal and, unless relieved, pressure on the original pressure side will build up until breakage occurs at some plate.

It is to be noted that, with a pump of sufiicient size not only may the motor A be operated but one or more other motors may" also be operated each having a pressure controlling valve and a Feet head equals:

5 valvecontrolling the direction of flowthrough the particular motor connected thereto. Also those other motors may be of any size or horsepower desired to agree with the purposes for which they are individually used.

In order to demonstrate the advantages of the plant shown in Fig. 12 the following is submitted, the dimensions of the parts and their capacities bein'g'taken from an actual working example of a plant constructed as in Fig. 12. I

Horse-power required, to pump per minute fifteen gallons of oil at 7.55 lbs. 7 per gallon at 80 lbs. gage pressure allowing 10% friction loss. Lbs. pumped equals 7.55 or 113.25.

80 lbs. plus 10%:88 inch lbs. gage pressure Each pound gage pressure is the equivalent of 2.31 feet of head so Total head=88 2.31 or 203.28 feet head Total weight feet head equals 203.28xl13.25=

23021.46 which divided by 33,000 equals horsepower output of pump or .69768 H. P.

There is thus delivered to the motor per minute 15 gallons at 88 lbs. gage pressure from which we may subtract a friction loss of 10 lbs. so that the working pressure is 80 lbs.

Thus a relatively small pump will acutate a relatively large motor.

While a concrete example has been given above the general formulae for these calculations may be written thus:

For pump output Where G is gallons pumped per minute W is weight per gallon P is gage pressure Formula foot pounds PXAXDXRPM 33,000 12 Where P=Pressure in lbs. per square inch80 lbs.

A=Constant minimum area exposed to pressure1.2 sq. in.

D=Distance travel per revolution-11 RPM=Revolutions per minute=303 As previously stated this motor may be used as a pump because when driven by a suitable motor the blades will act to suck in liquid as they leave the high points and express the liquid toward the high points of the stator.

Under the present arrangement as here shown with nine blades and six cam segments on each side the rotation of the rotor, acting as a pump will fill and discharge in each revolution six times nine times 2 the cubical capacity of the segments between the ports. The pumping capacity of this motor is established by the following formula:

wherein C=cubical content between ports per segment cubic inches H =number of segments per side B==No. of blades RPM=revolutions per minute In view of the above it will be noted that not only the eificiency but also the capacity as to size of pump is very high. What is claimed is:

1. In a device of the kind described, a stator including an annular body portion open at both sides, a pair of cam plates engaging against the stator body around the side openings thereof, each ,of said plates carrying on their inner faces a sinuous circular cam having high andlow points with the high points projecting into the stator body, the high points of each cam being opposite to the low points of the other, and a pair of heads engaging against the outer faces of the cam plates, said heads each having on its inner face a pair of annular and radially spaced grooves concentric to the axis of the plate, and supply and exhaust connections leading to said grooves, said plates each having ports leading from one groove of each pair of said grooves and opening through the high points of the respective cam at one side of each high point and having other ports leading from the other of said pair of grooves and opening through the high points of the last mentioned cam at the other side of each high point, in combination with a rotor mounted in the stator and having a slotted peripheral portion extending between said cams, and a series of blades slideably mounted in said slots and engageable at opposite edges with said cams.

2. In a device of the kind described, a stator including an annular body portion open at both sides, a pair of cam plates engaging against the stator body around the side openings thereof, each of said plates carrying on their inner faces a sinuous circular cam having high and low points with the high points projecting into the stator body, the high points of each cam being opposite to the low points of the other, and a pair of headsengaging against the outer faces of the cam plates, said heads each having on its inner face a pair of annular and radially spaced grooves concentric to the axis of the plate, and supply and exhaust connections leading to said grooves, said plates each having ports leading from one groove of each pair of said grooves and opening through the high points of the respective cam at one side of each high point and having other ports leading from the other of said pair of grooves and opening through the high points of the last mentioned cam at the other side of each high point, in combination with a rotor mounted in the stator and having a slotted peripheral portion extending between said cams, and a series of blades slideably mounted in said slots and engageable at opposite edges with said cams, the slotted peripheral portion of the rotor being in contact with the high points of each cam.

3. In a device of the kind described, a stator including an annular body portion open at both sides, a pair of cam plates engaging against the stator body around the side openings thereof, each of said plates carrying on their inner faces a sinuous circular cam having high and low points with the high points projecting into the stator body, the high points of each cam being opposite to the low points of the other, and a pair of heads engaging against the outer faces of the cam plates, said heads each having on its inner face a pair of. annular and radially spaced rooves concentric to the axis of the plate, and supply and exhaust connections leading to said grooves, said plates each having ports leading from one groove of each pair of said grooves and opening through the high points of the respective cam atone side of each. high point and having other ports leading from the other of said pair of grooves and opening through the high points of the last mentioned cam at the other side of each high point, in combination with a rotor mounted in the stator and having a slotted peripheral portion extending between said cams, and a series of blades slideably mounted insaid slots and engageable at opposite edges with said cams, the slotted peripheral portion of the rotor being in contact with the high points of each cam, said blades including cams.

CARL ZOLL.

References Cited in the file of this patent UNITED STATES PATENTS Number- Number Name Date Tucker et a1 Apr. 5, 1949 Tucker et a1; Apr. 5, 1949 Jones July 12, 1949 FOREIGN PATENTS.

Country Date Great Britain -i Oct. 6, 1921 Great Britain v Apr. 13, 1939 France June 1, 1944

Images