US3086475A - rosa en - Google Patents

Description

April 23, 1963 o. E. ROSAEN VARIABLE DELIVERY PUMPS 3 Sheets-Sheet 1 Filed Dec, 19. 1955 ow mom 5 INVENTOR. OSCAR E. ROSAEN ATTORNEYS April 23, 1963 o. E. ROSAEN VARIABLE DELIVERY PUMPS Filed Dec. 19, 1955 3 Sheets-Sheet 3 INVENTOR. OSCAR EJROSAEN ATTORNEYS United States Patent 3,086,475 VARIABLE DELIVERY PUMPS Oscar E. Rosaen, 51 Cloverly Road, Grosse Points 36, Mich. Filed Dec. 19, 1955, Scr. No. 557,222 2 Claims. (Cl. 103-436) The present invention relates to fluid pumps of the vane type and more specifically to such a pump provided with means whereby to control the output.

Among the objects of the invention is to provide in a pump of the kind indicated, a simple adjusting means by which. the volume of fluid moved per revolution of the rotor may be varied from full capacity to zero.

Another object is to simplify the construction of such a pump and thereby to reduce the cost of production.

Another object is means by which the pressure of the vanes against the surrounding .ring may be controlled.

Other objects and advantages will readily occur to those skilled in the art upon reference to the following description and the accompanying drawings in which- FIG. 1 is a longitudinal section of the pump on line 11 of FIG. 2.

FIG. 2 is'a vertical section on line 2-2 of FIG. 1.

FIG. 3 shows in elevation the right hand cheek plate of FIG. 1 with certain other parts in section.

FIG. 4 is a view as from the bottom of FIG. 3.

FIG. 5 is a view in "elevation of the cam ring and rotor.

FIG. 6 is a view from the bottom of FIG. 5.

FIG. 7 is a view in elevation of the inner face of the left hand cheek plate of FIG. 1.

FIG. 8 is a view in elevation of the outer face of the. same.

FIG. 9 is a side view of the rotor partly in section.

FIGS. 10 and 11 are respectively side and end elevational views of one of the vanes.

FIG. 12 is a view in elevation of the control valve and FIG. 13 is a partial view of the outer face of the same.

FIGS. 14 to 18a inclusive show several forms of vanes which may be used.

FIG. 19 shows a portion of a reversible rotor and cam ring.

In the drawings, the pump is shown as comprising a housing consisting of two parts, a main portion A and a cap member B. The portion A is provided with an axial opening in which is mounted a drive shaft C, a suitable anti-friction bearing D and oil seal H being mounted in an enlarged portion of the axial opening. The shaft C extends through the housing portion A and into a recess 20 in the cap B, a suitable plain bearing 20A receiving the shaft end in the recess, the bearing 20A being provided with a shoulder 20B abutting a coacting shoulder in the recess to position the bearing and prevent free access of fluid to the recess.

The housing portion A is provided with a fluid inlet E and outlet F. The housing portion A is provided with a cylindrical bore, with which the shaft is coaxial, and has mounted within the bore the active working parts of the pump comprising the cheek plates 21 and 22, the cam ring 23 and the rotor 24. The cheek plates and cam ring are fixed together With the camring between the plates and the rotor is within the ring.

As shown, the cheek plate 21 is provided with a rather large hub portion 21A having a sufiiciently large axial opening to receive the outer race of a roller bearing 21B, the inner race of which is a sleeve 21C keyed to the shaft C and sleeve 21C is provided at the end adjacent the rotor 24, with teeth 21D interfitting with similar teeth 24A carried by the rotor 24. The outer end of hub 21A extends into an enlarged recess in cap B but is spaced therefrom for a purpose to be described later.

The check plate 21 is also provided with a substantially radially arranged conduit 21E opening to the inner face of. the plate at 21F, the opening being arcuate and so located as to register with the bottom portions of the vane slots in the rotor 24. The plate 21 is also provided with a small through passage 21G near its periphery.

The check plate 22, shown in elevation in FIG. 8, is provided in its inner face with a recess 22A somewhat greater in diameter than the shaft C, and has a radially arranged conduit 22B leading from the recess to near the periphery and opening through a lateral passage 22C to the outlet F.

The plate 22 is also provided in its outer face with a channel 22D extending inwardly from the periphery and with a plurality of small through passages 22E spaced evenly about the central recess and so located as to register with the bottom portions of the vane slots in the rotor. These passages 22E have the same spacing as the vane slots but are less in number than the slots, the first one of the series, designated 122E, being so located as to be approximately opposite but out of registration with the opening 21F in the direction of rotation of the rotor by a distance somewhat less than the diameter of the enlarged bottom portion of the vane slot.

The inner face of plate 22 shows the inner ends of the passages 22E to be enlarged in the direction of rotation of the rotor as at 22F and also shows a larger opening 22G of the same size and at a location opposite the opening 21F in plate 21. This opening 22G communicates with the passage 22H leading to the periphery of the plate 22. The plate is also provided with a small through passage 22M.

The cam ring 23 consists of a hardened steel ring of suitable width axially and of varying thickness radially so that the inner periphery forms a spiral from about the point N clockwise to about the point P. The surface from about the point P to the point 0 is on a fixed radius about the center and from the point 0 to the point N the surface is on an increasing radius so that this ramp portion merges smoothly into the arcuate and spiral por tions.

The ring 23 is also provided with more or less tangentially arranged passages 23A from the outer to the inner peripheries of the ring and through the ramp portion (from O to N). There is also a passage 2313 to the outer periphery arranged tangentially at right angles to the axes of passages 23A just beyond the latter in the direction of rotation of the rotor, and the ring is provided with a small passage 23C extending axially.

The rotor 24 is shown in FIGS. 1, 5 and 9. This consists of a disc mounted on shaft C and driven thereby as mentioned above. The outer periphery of the disc is provided with equidistant radial slots 24B in which are slidably carried vanes 25, the slots being enlarged at their bottoms as shown. Radially inward of the slots 24B and opposite the spaces between the slots, the disc is provided with a plurality of passages 24C opening to that,

face adjacent cheek plate 22 and connected to radial passages 24D opening to the periphery of the disc between vane slots 24B and preferably widened as shown.

For a purpose to be described later, each of the vane slots, as shown in FIG. 9, may be connected through a small passage 24E to the periphery of the disc ahead of and behind its vane, the passage leading laheadof the vane being smaller in capacity than the other.

In the rotor of FIG. 5, the passages 24E have been omitted and in the rotor of FIG. 19 the passages 124E are of the same size.

The just mentioned differences in the rotor require 3 different forms of vanes and several vanes are shown in FIGS. 10, 11 and 14 to :18.

In FIGS. 14 and 14A is shown the form of vane indicated at 25 in FIG. 9. This consists of a rectangular metal plate having one edge bevelled as at 25A, this being the edge contacting the cam ring 23. FIG. 14 is a side view and FIG. 14A is a bottom end view of such a vane.

The vanes for use with rotors not provided with passages 24E are shown in FIGS. l0, 11, 16, 17 and 18.

In FIGS. and =11, showing respectively a side and end view of a vane, the plate 125 constituting the vane has one edge 125A bevelled at a large angle. This is the outer edge of the vane contacting the ring 23 with the face of the bevel trailing. (See FIG.5.) The vane 125 also has the lateral edges of the front end rear faces also bevelled, the bevels 125B at the shorter or trailing face being somewhat larger than those 125C at the longer or forward face. This form of vane is shown in FIG. 5.

As indicated in FIG. 19, in those pumps in which the rotor is reversible, the passages 124E corresponding to passages 24E are preferably of the same size both forward and behind the vanes and a vane such as is shown in FIGS. 15 and 15A is used. These show respectively a side and bottom end view of the vane which consists of a rectangular plate 150 having one edge double bevelled as at 150A, the two bevel faces being substantially equal.

In FIGS. 16 and 16A, the vane '160 is double bevelled at 160A as is that in FIG. 15 but are shown as having the four later-a1 corners chamfered as at 160B, the chamfers being equal.

In FIGS. 17 and 17A, the vane 170 is also double beveled as at 170A, but, instead of chamfering the corners, a small passage 170B extends from each of the bevel faces to the lower end of the vane. These passages are shown as of equal size.

In FIGS. 18 and 18A the vane 180 is double bevelled at one end as at 180A and provided with a groove 180B in each side face extending lengthwise from a bevel face to the rear end. The grooves are shown as equal in size.

Fixed to the rotor disc and rotating therewith is a valve edge carrying a plurality of spring pressed iball valves 30A adapted to close the ends of passages 24C. The cage and valves are located in the recess 22A in plate 22 which, as stated above, communicates with the outlet F through passages 22B and 22C.

The housing member A is provided with an axial recess which is open to the inletE through the channel 22D and in this recess is mounted for rotation a ring 36 which is spaced from the peripheral wall of the recess and carried upon a sleeve 37 in turn carried upon a bushing 38, the latter extending into the axial opening in plate 22.

The ring 36, as shown more in detail in FIGS. 12 and 13, is rectangular in cross section and provided on its outer periphery with a short gear segment 36A. It is also provided with a plurality of axially extending through passages 363 into which lead radial passages 36C and upon the face adjacent plate 22 the passages 36B are slotted as shown at 36D in FIG. 12, the slots being graduated in length, each slot being somewhat shorter than the preceding slot (moving clockwise of FIG. 12). These slotted passages are equal in number and spacing to the spaced passages 22E in plate 22 and so located as to register therewith when the ring 36 is in one extreme position of partial rotation.

However, the slots 36D are so proportioned that, when the ring is in its other extreme position, all of the passages 22E are closed, and progressive rotation of the ring opens the passages progressively. For example the first slot 36D upon moving the ring 36, opens the first passage 22E and is long enough to maintain it open as the ring is moved around. Further, when the second passage is opened, it also remains open with further movement of the ring and so on until all of the passages 22E are open.

Rotation of ring 36 may be accomplished by means of a rack 40 coacting with the gear segment 36A and ex- 4 4 tending to the outside of the housing through a suitable packing 41 and operable by a lever 42.

In the operation of the pump, with suitable motive power applied to shaft C rotating the shaft and the rotor 24, fluid will enter the inlet E and its lateral extension EE and pass into the rotor chamber through the passages 23A which lead to the intravane spaces. At the same time,-

the fluid will flow through the passages 21E (plate 21) and 22H (plate 22) to the bottoms of the vane slots 24B,

causing the vanes 25 to move outwardly.

With the ring 36 in the position indicated in FIGS. 2 and 12, that is, in the position in which all of the passages 22B are closed, the vanes will be held out against the cam ring 23 from about the point N and the pump will operate at full capacity.

When the ring 36 is rotated by the rack 40 to open one or more of the passages 22E, the vanes will not begin actively moving fluid until later, depending upon the number of passages 22E that have been kept closed. The output of the pump may therefore be adjusted from full capacity to substantially zero capacity. With the adjustment for full or partial output, pressure in the outlet passage 2213 will produce pressure in the small conduit 22M23C-21G leading to the chamber 45 outside of check plate 21 and force the cheek plate and cam ring assembly toward the left (FIG. 1) and any leakage from this chamber past the bushing 20A into the recess 20 in housing member B, will be returned to the inlet E through passage 46. Leakage at the other end of the shaft, past the bushing 38, will also be returned to the inlet B through passage 47.

Provision is also made to eliminate solid particles entering the pump by arranging the tangential passage 23B just beyond the fluid inlets 23A in the ring 23. As the fluid flows in through the inlets 23A and is moved rapidly clockwise (FIG. 5), the solid particles will be thrown into the passage 23B and be collected in a small chamber 49 provided in housing A and normally closed by a plug 48.

It will be noted that three forms of rotor are shown. The one in FIG. 5 is indicated as without the passages 24E or 124E while the rotor of FIG. 9 is provided with the passages of different size and that of FIG. 19 shows similarly located passages 124E but of the same size. It will also be noted that the vanes of FIGS. 5, 10 and 11 with the chamfered corners provide fluid conduit means leading from the periphery of the rotor to the bottoms of the vane slots ahead of and behind the vanes with respect to rotor rotation. Like the vanes of FIGS. 16 to 18 they are provided with chamfers or passages located so as to provide conduit means leading from the bottoms of the vane slots to the periphery of the rotor ahead of and behind the vane.

The purpose and function of the passages 24E, 124E and the chamfering is to control the force between the outer edge of a vane and the cam ring 23.

If, as is commonly done in pumps of the vane type, the back pressure from the delivery is utilized to hold the vanes out against the ring, the pressure between vane and ring is so high that excessive wear of these parts reduces the life of the pump, and delivery pressures must, therefore be lowered.

I claim:

1. Vanes for use in a fluid pump of the vane type wherein a rotor carrying radially slidable vanes in slots in its periphery is surrounded by a cam ring contacting the outer edges of said vanes and determining the radial position thereof, said vanes comprising rectangular plates having their ring contacting outer edges bevelled and having the lateral edges of their faces bevelled to thereby form continuously open passageways leading from the pumping chamber to the inner end of the vane slots both ahead of and behind the vanes to control the pressure acting on the inner end of said vanes.

2. Vanes for use in a fluid pump of the vane type wherein a rotor carrying radially slidable vanes in slots in its periphery is surrounded by a cam ring contacting the outer edges of said vanes and determining the radial position thereof, said vanes comprising rectangular plates having their ring contacting outer edges bevelled and having the lateral edges of their forward faces bevelled, and also having the lateral edges of their rearward faces bevelled but to a greater degree to thereby form continuously open passageways leading from the pumping chamber to the inner end of the vane slots both ahead of and behind the vanes to control the pressure acting on the inner end of said vanes.

References Cited in the file of this patent 6 Vickers Feb. 21 1933 Wade Feb. 26, 1935 Livermore Mar. 31, 1942 Rosen Jan. 15, 1946 Stephens June 14, 1949 MacMillin et a1. Mar. 13, 1951 Senninger Nov. 13, 1951 Ernst Sept. 30, 1952 Ernst Sept. 30, 1952 Vincent Dec. 23, 1952 Minshall Oct. 6, 1953 Garner Oct. 27, 1953 Gassot Aug. 30, 1955 Kovach Oct. 4, 1955 Lindberg Dec. 27, 1955 Prendergast Jan. 24, 1956 FOREIGN PATENTS Great Britain of 1911 Great Britain Jan. 2, 1946 France Nov. 18, 1930 France Feb. 10, 1931

Claims (1)

1. VANES FOR USE IN A FLUID PUMP OF THE VANE TYPE WHEREIN A ROTOR CARRYING RADIALLY SLIDABLE VANES IN SLOTS IN ITS PERIPHERY IS SURROUNDED BY A CAM RING CONTACTING THE OUTER EDGES OF SAID VANES AND DETERMINING THE RADIAL POSITION THEREOF, SAID VANES COMPRISING RECTANGULAR PLATES HAVING THEIR RING CONTACTING OUTER EDGES BEVELLED AND HAVING THE LATERAL EDGES OF THEIR FACES BEVELLED TO THEREBY FORM CONTINUOUSLY OPEN PASSAGEWAYS LEADING FROM THE PUMPING CHAMBER TO THE INNER END OF THE VANE SLOTS BOTH AHEAD OF AND BEHIND THE VANES TO CONTROL THE PRESSURE ACTING ON THE INNER END OF SAID VANES.

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