US2755744A

US2755744A - Rotary hydraulic ratio pump

Info

Publication number: US2755744A
Application number: US318648A
Authority: US
Inventors: Alvin G Halvorsen
Original assignee: Individual
Current assignee: Individual
Priority date: 1952-11-04
Filing date: 1952-11-04
Publication date: 1956-07-24
Anticipated expiration: 1973-07-24

Description

y 24, 1956 A. G. HALVORSEN 2,755,744

ROTARY HYDRAULIC RATIO PUMP Filed Nov. 4, 1952 2 Sheets-Sheet 1 INVENTOR ,4: WV 5 #41 V0255 BY ww m l/j ATTORNEY July 24, 1956 A. G. HALVORSEN 2,755,744

ROTARY HYDRAULIC RATIO PUMP Filed Nov. 4, 1952 2 Sheets-Sheet 2 INVENTOR 41 w/v G L/AL V025N m5 ATTORNEY United States Patent ROTARY HYDRAULIC RATIO PUMP Alvin G. Halvorsen, Houston, Minn.

Application November 4, 1952, Serial No. 318,648

3 Claims. (Cl. 103-121) This invention relates to a rotary hydraulic ratio pump, and has for one of its objects the production of a pump which may be used as an hydraulic all ratio transmission automatic pump, as an hydraulic motor and motor meter, as a ratio hydraulic lift, as a water pump, and for other purposes.

A further object of the present invention is the production of a simple and efiicient pump having an outer rotor and an inner eccentrically mounted rotor, the outer rotor carrying a hinged vane which is slidable in the inner rotor and the outer rotor also carrying vanes which are hinged to constitute swinging gate vanes loosely fitting in sockets formed in the inner rotor in a manner whereby the outside rotor may be used to provide outside power when used as a motor, the eccentric mounting of the inside rotor controlling the inside rotor.

Other objects of the present invention will appear throughout the following specification and claims.

In the drawings:

Figure 1 is a side elevational view of the pump casmg.

Figure 2 is an edge elevational view thereof, certain parts being shown in section.

Figure 3 is a side elevational view of the inner and outer rotors.

Figure 4 is a diagrammatic view illustrating the movement of the eccentric.

Figure 5 is a diagrammatic view illustrating a movement of the eccentric and the operating lever movement.

Figure 6 is a further diagrammatic View illustrating a different position of the lever and eccentric.

Figure 7 is a side elevational view of the outer rotor, partly in section.

Figure 8 is a side elevational view of a modified type of inner rotor.

Figure 9 is a side elevational view of one of the guide members for the vanes which engage the inner rotor;

Figure it) is an end view of one of the guide members, the vane being shown in transverse section.

By referring to the drawings in detail, it will be seen that it; designates the outer casing or housing of the pump which is provided with a cover plate 11. The cover plate 11 is secured to the casing or housing 10 by means of suitable bolts 12. The cover plate 11 is provided with an inlet pipe 13 and an outlet pipe 14 which communicate with the interior of the casing 10 for the admission of fluid to and from the interior of the casing 10 under the action of rotation of the rotors hereinafter described. The pipes 13 may be used as an outlet and the pipe 14 may be used as an inlet, if desired, the use of the pipes being reversed within the spirit of the invention and being optional.

An outer rotor 15 is mounted within the chamber 16 of the casing and the

pipes

13 and 14 communicate with this chamber 16 to carry the flow of fluid to and from the chamber 16 in a conventional manner. Wedge-like gaskets or

sealing rings

17 and 18 are interposed between the outer rotor 15 and the cover plate 11, as is shown in Figure 2, to provide a fluid seal therebetween. One face of each ring is at an approximately 30 angle, as shown in Figure 2, to provide a maximum seal between the rotor and the cover plate.

The outer rotor 15 is provided with a chamber 19 in which is eccentrically mounted the inner rotor 20. An elongated primary vane 21 is hingedly secured to the outer rotor 15 by means of a hinging head 22 which fits within a circular socket 23 formed in the outer rotor 15, as is shown in Figure 3. The socket 23 is provided with

flaring walls

24 and 25 to provide a flaring communicating opening from the socket 23 with the chamber 19. These

walls

24 and 25 are preferably 37 /2 degrees or maybe 45 degrees of angle to permit the vane 21 to freely swing. The vane 21 is provided with a tapering neck 26 adjacent the hinging head 22, the sides of the neck conforming to the angle of the

walls

24 and 25 to prevent interference with the swing of the vane 21.

The inner rotor 20, which is eccentrically mounted within the chamber 19 of the outer rotor 15, is provided with a transversely extending slot 27 in which one end of the vane 21 is slidably mounted, as is shown in Figure 3. The outer rotor 15 is provided with fluid recesses 28 which communicate with the chamber 19 and extend to points in close proximity with the

respective pipes

13 and 14 to facilitate in and out flow of fluid from the chamber 19. These recesses 28 taper as at 29 at the ends thereof.

The inner rotor 20 is provided with angularly radiating spaced vane receiving recesses or pockets 30 and 31, into which the respective small auxiliary gate vanes 32 and 33 fit in the manner shown in Figure 3. The pockets are of greater size than the vanes 30 and 31. The vane 32 is hingedly secured to the outer rotor 15 by means of the hinging head 34 fitting in the circular socket 35. The vane 32 is provided with a tapering neck 36 leading to the head 34 and the socket 35 is provided with diverging walls 37 at an angle radiating preferably at 37 /2 degrees to facilitate free swing of the gate vanes 32 and 33. The vane 33 is similarly constructed and mounted as is shown in Figure 3.

The outer rotor 15 is provided with a shaft 38 which extends through a bearing 39 and the eccentrically mounted inner rotor 20 is provided with a shaft 40 which extends through a bearing 41. A suitable lever 42 may be secured to the shaft 40 to facilitate the control of the eccentric bearing.

It should be understood that the vane 21 which is hinged to the outer rotor 15 and which slidably fits in the slot 27 of the inner rotor 20 will hold the inner rotor steady while the pump is in operation. The small swinging gate vanes 32 and 33 provide a means to cause the pump to run smoothly. The wedge-like tapering gaskets or

sealing rings

17 and 18, the taper of the rings being approximately 25 to 30 degrees to adequately seal the junction of the cover plate 11 with the casing or housing 10.

The operation of the pump is as follows:

It should be understood that the outer rotor 15 and the inner rotor 20 are in the positions shown in Figure 3 when pumping starts. The arrow indicates direction of rotation. The fluid enters inlet 13 and passes out through outlet 14 and the swinging gate vane 21 forms a vacuum on one side thereof while on the reverse side it creates pressure. The vanes 32 and 33 then swing shut against the inner rotor 20 to create pressure on one side thereof and a vacuum on the other side thereof. The entrances of the slot 27 and recesses or pockets 30 and 31 are equally spaced from each other.

In Figure 4 the arrow indicates one half movement of the eccentric and is accomplished by a A; drop in its distance of movement on the end plate of the device and firth drop in its distance of movement on the eccentric.

By moving the eccentric a distance of /tfll of its distance of movement, this permits the inside rotor to center. The vertical lines A and B show the otf set position to one side of the normal center for centering the inner rotor 20 within the outer rotor 15. The line A indicates the center or" the cover or end plate 11 for the pump and the line B shows the distance of movement of the cocentric which is approximately in a straight line to the right of line A. The inlet and outlet are indicated by the arrows which are properly designated. It should be noted that the vanes 32 and 33 during operation swing shut from rotation of the outer rotor with respect to the vane 21 which vane 21 pulls the inner rotor along to provide rotary motion. The vanes 32 and 33 shut from the pressure or vacuum depending upon the use of fluid or air. The outer rotor may be rotated or driven in any desired manner, and the inner rotor is driven by means of the vane 21.

In Figure there is shown the position of the rotor 20 with a Ath of the distance of movement of the cam actuating lever 42.

In Figure 6 the eccentric is shown with a /3 distance of swing of the eccentric lever. This is accomplished by moving the eccentric 3/ of an inch down and of an inch to one side. Since the eccentric is also of an inch, this moves the inner rotor 20 in practically an up and down movement inside of the rotor 15, as shown in the dotted position.

The fluid enters the inlet in a conventional manner and when the pump rotates in either direction a vacuum is created upon one side of the vanes and a pressure on the other, and vice versa when reversed. When the inner rotor 20 is raised, the pumping is less, and when it is lowered, the pumping is in greater volume. When the eccentric is turned all the way down, the pump actuates rapidly but requires more power to operate the same.

In Figure 8 there is shown a modified form of inner rotor, wherein the rotor 20:; is provided with a slot 43 similar to the slot 27. Circular cavities 44- and 45 are provided in place of the pockets 30 and 31 shown in Figure 3.

Guide members

46 and 47 are fitted in these

cavities

44 and 45 respectively. The

cavities

44 and 45 are less than completely circular and slightly more than semi-circular, thereby defining restricted openings to retain the guide members against accidental displacement as shown in Figure 8. Vanes similar to the vanes 32 and 33 fit within the

slots

48 and 49 which are formed in these

members

46 and 47. When the device is used as a water pump the inner rotor may be made of plastic if desired. The

guide members

46 and 47 are similarly constructed, and attention is invited to Figures 9 and which illustrate the construction of the guide member 46. The guide member 46 comprises a cylindrical body having a longitudinal slot 48 open on one side and closed at the other side by a bridge portion 50. The guide member 46 is provided with a similar slot 49. A vane 32a similar to the vane 32 fits in the slot 48 of the guide member 46 and a vane 33a fits in the slot 49 of the guide member 47. This structure provides a smoothly running pump.

The recess 28 formed in the inner face of the'outer rotor provides a fuel reservoir or receiving recess to contain an adequate amount of inlet and outlet fluid. This is of advantage in a rotary motor where the inlet and outlet openings cannot be too long or too large because of lack of space. If the openings are too long or too large, one opening will interfere with the other opening and efficiency will be lost. Furthermore, the recesses permit pressure to be directed against the outside rotor when the pump runs at a high rate of speed during which time the inlet vacuum pull will be at a maximum and the recess openings will be completely filled with fluid. When the recess openings are completely filled, the outer rotor will operate as if no recesses were formed therein, until the fluid is removed or is in the process of being removed.

I claim:

1. A pump of the class described comprising a casing, fluid inlet and outlet ports for said casing, an inner rotor, and an outer rotor mounted in said casing, said inner rotor being eccentrically mounted in said outer rotor, said outer rotor having a concentric fluid recess upon its inner face intermediate the inner eccentric rotor said said outer rotor, thereby defining a reservoir fuel channel therebetween in which an adequate amount of fuel is compressed as the inner eccentric rotor moves toward the recess of the outer rotor upon rotation, the inlet and outlet ports communicating with said recess, a primary vane hinged to the outer rotor and slidably en-. gaging the inner rotor to steady the inner rotor, a plurality of auxiliary vanes hinged to the outer rotor and loosely engaging the inner rotor for facilitating the smooth running of said pump, the fluid being adapted to be compressed within said recess between the rotors as the inner eccentric rotor rotates within the outer rotor.

2. A pump as defined in claim 1, wherein the inner rotor is provided with circular cavities having restricted openings, guide members rotatably mounted in said cavities of said inner rotor, each guide member being formed of one piece, and said auixiliary vanes being slidably mounted through said guide members.

3. A pump as defined in claim 1, wherein the casing is provided with an open side, a cover plate closing said open side, and wedge-like gaskets defining scaling rings interposed between said outer rotor and said cover plate, said gasket having an inclined face at an angle of approximately 30".

References Cited in the file-of this patent UNITED STATES PATENTS 1,352,107 Wagenhorst Sept. 7, 1920 1,695,650 'Godillot Dec. 18, 1928 1,806,206 Lees May 19, 1931 1,828,245 Davidson Oct. 20, 1931 1,961,592 Muller June 5, 1934 FOREIGN PATENTS 266,514 Great Britain Mar. 3, 1927 848,518 France July 24, 1939