US2937599A - Fluid pump - Google Patents

Fluid pump Download PDF

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US2937599A
US2937599A US530495A US53049555A US2937599A US 2937599 A US2937599 A US 2937599A US 530495 A US530495 A US 530495A US 53049555 A US53049555 A US 53049555A US 2937599 A US2937599 A US 2937599A
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passages
fluid
chamber
ring
rotor
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US530495A
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Oscar E Rosaen
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Oscar E Rosaen
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C20/00Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/10Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F01C20/14Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using rotating valves
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01CROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08Rotary pistons
    • F01C21/0809Construction of vanes or vane holders
    • F01C21/0818Vane tracking; control therefor
    • F01C21/0854Vane tracking; control therefor by fluid means
    • F01C21/0863Vane tracking; control therefor by fluid means the fluid being the working fluid

Description

0. E. ROSAEN May 24, 1960 FLUID PUMP 2 Sheets-Sheet 1 Filed Aug. 25, 1955 ATTORNEYS I 0. E. ROSAEN FLUID PUMP May 24, 1960 2 Sheets-Sheet 2 Filed Aug. 25, 1955 INVENTOR.
OSCAR E.ROSAEN %A %J44 ATTORNEYS Unite States 4 Patent FLUID PUMP Oscar E. Rosaen, 51 Roslyn Road, Grosse Pointe 36, Mich.
Filed Aug. '25, 1955, Ser.'N0. 530,495
Claims. (Cl. 103-120) The present invention relates to .fluid pumps of the vane type in which radially slidable vanes in a rotor contact a surrounding cam ring and are gradually moved inwardly to decrease the chamber between the vanes and force out the fluid.
Among the objects of the invention is to provide means whereby the pump delivery may be varied at will although the rotor speed remains constant.
Still other objects 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 sectional view on the line 1-1 of Fig. 3.
Fig. 2 is a view in elevation of the regulating ring and associated parts as viewed from the right of Fig. '1 with the end housing member removed.
Fig. 3 is a view in elevation of the rotor and cam ring with parts in section on line 3-3 of Fig. 1.
Fig. 4 is a view in elevation from the right of 'Fig. l, of the right hand cheek plate of Fig. 1.
Fig. 5 is a fragmentary view in elevation of the regulating ring.
Fig. 6 is a plan view of an outlet valve plate.
In Fig. 1 of the drawings, the pump is indicated as consisting of a housing 10 having a fluid inlet 10A provided with branches 1013. The end of the housing is closed except for the axial opening receiving the shaft 11 mounted in a suitable bearing 11A. An oil seal 11B prevents escape of fluid around the shaft. Within the housing the shaft passes through and is splined in the rotor 12 and at its end is seated in a bushing 11C carried in the housing closure plate 10C which is alsojp'rovided with a fluid outlet 10D. 7
' The rotor 12 consists of a disc-like member provided with cylindrical axial extensions 12A and 12B and these are mounted in roller hearings in the cheek plates 14 and 15. Between the cheek plates 14 and 15 and surrounding the rotor 12 is a cam ring 16, the ring and rotor "disc being of such thickness dimension as to provide a close sliding fit of the rotor disc between the cheek plates when these several parts are held together in the housing.
Surrounding the shaft opening in housing 10 is a small chamber 17 and in this chamber is located a floating bushing 17A having a flange abutting a suitable shoulder 'in the housing wall and held against the shoulder by a suitable spring 1713, the other end of the spring abutting an annular plate 170 lying against the check plate 14. The chamber 17 is in communication with the space in which lies the cheek plate 14 so that fluid under pressure in the chamber tends to force the cheek plate toward the cam ring 16.
' The other cheek plate 15 by means of a suitable roller bearing supports the rotor extension 12B and is provided with a plurality of evenly spaced through passages 20, while both cheek plates are provided with radially arranged passages 21-21A, opening to the branch inlet passages 10B, and areuate openings 22 leading'to the 2 rotor chamber. The two cheek plates 14 and 15 and ring 16 are accurately positioned relative to each other and to the housing by means of a dowel 110.
The discportion of rotor 12-is provided in its periphery with a plurality of radial slots in which are slidably mounted vanes 12A and each slot terminates at its bottom in an enlarged through passage 23, the passages 23 in the rotor and the passages 22 in the cheek plates being so located as to register. Also adjacent each vane slot and leading from its bottom 23 to the periphery of the rotor disc ahead of the vane is a small passage 24. Y
' Between each two vane slots is provided a radial passage 25 leading from the periphery of the disc to the axial opening in'the rotor. The axial opening in the rotor is provided with splines for about half its length to fix it to the shaft 11, the other portion being smooth and spaced from the shaft 'to' provide an annular outlet chamber 26 into which the passages '25 open, the latter being valved as shown at 25A in Fig. 3. The valve 25A maybe a plate valve actuated by a suitable spring 255. The form of plate is shown in Fig. 6.
The chamber 26 opens to the end of the axial rotor extension 12B and into an annular outlet or discharge chamber 27 communicating with the outlet 10D. The chamber 26 is also connected to the chamber 17 by one or more longitudinal slots 26A so as to provide pressure in the latter chamber. Y
The end of the shaft 11 as mentioned above, is seated in a bushing 11C and the bushing itself is seated upon a suitable shoulder in the inner face of the closure plate 10C being held against the shoulder by a suitable spring 28 abutting against the cheek plate 15. Any fluid leaking past the bushing 11C will flow into a small chamber 29 opposite the end of the shaft and through the axial end of the shaft bore 30 in the shaft 11 and pass out through the lateral opening 31 into the small chamber between bushing 17A and the oil seal 11B and out 9 through the drain 32. V
Carried in a suitable recess in the inner face of closure plate 10C and rotatably mounted upon an axially extending flange 35 on cheek plate 15 is a ring 40 provided with a short segment of gear teeth 41 which mesh with a small gear 42 fixed to or made integral with a short shaft 43 extending through the closure plate'lOC and provided with a suitable handle or lever 44.
This ring 40 is of such outer diameter as 'to provide an encircling space or chamber 45 in the recess in which the ring is mounted. It is also provided with openings or passages 46 arranged axially of the ring to which are connected other passages 47 leading radially to the chamber 45. The ring 40 is so located that the passages 46 are adapted 'to register with the passages 20 through cheek plate 15 and it should be noted, these passages 46 are not all of the same sizebut gradually increase in their arcuate length from an area equal to that of one of the passages 20 to an area several times the area of "a passage 20.
In Fig. 3 the cam ring 16 is shown as provided with a main fluid inlet 50 and that the inner periphery of the ring is in the form of a spiral whose radius gradually decreasesclockwise-from the edge of the inlet 50'to a point ahead of the inlet and then is constant for a distance about equal to the distance between vanes. The radius then increases rapidly to provide a ramp between the short and long radius portions. The peripheral width of the inlet 50 is substantially equal to the length of the ramp; The passages 20 are evenly spaced and located opposite the spiral portion of the cam ring, with the first one 20A (see Fig.4) ashort distancebeyond (in the directionof rotation) the opening 22, the last one 20B,being a short distance ahead of the constant radius portion of the cam ring 16. The chamber 45 open to the radial passages in ring 40 connects through a passage 45A with the branch inlet passage 21A."
As shown in Fig. l, the passages 20 are of larger area at the end toward the pump chamber and the first one 20A, Fig. 4, is so located that the enlarged portion 23 of a vane slot reaches it immediately after leaving the inlet passage 22. The last one 20B of the passages 20 is located at the beginning of the circular portion of the cam ring.
With the ring 40 in place and the largest of the passages 46 adjacent the first passage 20A, rotary movement of ring '40 will progressively connect the passages 20 with the inlet branch passage 21A through the connecting passages 46, 47, 45, 45Afirst, one passage 20, then two, then three, etc. Or, all of the passages 20 may be maintained closed.
With this progressive closing of the passages 20, the pumping operation of the several vanes may be regulated to begin immediately after leaving the inlet 50 or delayed to begin at any later desired point on the spiral cam ring, thereby controlling the output of the pump. In the operation of the pump, with the rotor turning clockwise (Fig. 3) fluid will be drawn through the inlet and passage 50 into the intervane spaces and also through the passages 21-21A, 22 into the vane slots 23 as the vanes move outwardly following the cam ring.
As the slots 23 leave the passages 22, fluid is trapped under the vanes to hold them against the cam ring. As the cam ring radius decreases, the vanes are, of course, pushed into the slots, displacing the trapped fluid, some of which escapes through leakage but most of which passes through the passages 24 to the intervane space ahead of the vane, in which the pressure is higher than in the next succeeding space.
When the pressure in a space exceeds the spring pressure at the valves 25A, the fluid is of course expelled to the axial outlet.
The control ring 40 when in one extreme rotative position is set for maximum delivery and in its other extreme position is set for the minimum delivery. In the maximum delivery position, the ring is so set as to close all of the passages 20. However, movement of the ring 40, progressively opens the passages 20, opening first the passage 20 that is nearest to the inlet 50, so that the fluid in the vane slot is not trapped until vane slot has moved further upon the cam ring to the next passage 20 and as this is closed the fluid is trapped and pumping begins.
Further movement of the ring 40 will open a second and then a third and so on, those previously opened remaining open, so that it is possible to determine at what point upon the cam ring pumping will begin. Of course, opening a passage 20 permits the fluid in the vane slot to flow back to the fluid inlet through the passages 27, 45 and 45A.
I claim:
1. A fluid pump comprising a pair of cheek plates having a cam ring clamped therebetween and providing a chamber, a rotor in said chamber and comprising a disc having a plurality of radially arranged slots in its periphery with vanes slidably carried therein and contacting the inner surface of said ring, a fluid inlet to said chamber and to the intervane spaces therein, the said inner surface of said ring being in the form of a spiral for the major portion of its surface with the maximum radius portion of said spiral being adjacent said fluid inlet and with its radius decreasing in the direction of rotation of said rotor to a minimum radius portion at a point just short of said fluid inlet and ramp means connecting the surface at said last mentioned point and the surface at the point of maximum radius, fluid inlets through the cheek plates located to communicate with the radial inner end of said vane slots as the vanes pass successively over said ramp means to move said vanes outwardly, fluid outlet means from said chamber, one of said cheek plates being further provided with a plurality of passages therethrough communicating with the radial inner end portions of said vane slots while the vanes are passing through the working zone of said pump chamber between the fluid inlet and said point of minimum radius, conduit means leading from said plurality of passages to the pump inlet to thereby relieve the fluid,
pressure from being trapped beneath the vanes at the inner end of said slots to thus render the same inoperative for pumping fluid, and manually adjustable means positioned adjacent said last mentioned cheek plate and between the said passages and said conduit means to pre vent communication therethrough, said manually adjustable means being provided with a plurality of spaced openings therein of varying size progressively increasing in eflective area of opening and adapted to register with said passages of said cheek plate so that on adjustment of said means on opening will be brought to register first with a passage in the cheek plate when the vanes are contacting the ring surface of maximum radius and thereafter to progressively and selectively bring more of said openings into register with said check plate passages throughout substantially the entire pumping chamber to thereby vary as desired the point at which effective pumping action will begin in said chamber and hence to vary the delivery of said pump.
2. A fluid pump comprising a pair of check plates having a cam ring clamped therebetween and providing a chamber, a rotor in said chamber and comprising a disc having a plurality of radially arranged slots in its periphery with vanes slidably carried therein and contacting the inner surface of said ring, a fluid inlet to said chamber and to the intervane spaces therein, the said inner surface of said ring being in the form of a spiral for the major portion of its surface with the maximum radius portion of said spiral being adjacent said fluid inlet and with its radius decreasing in the direction of rotation of said rotor to a minimum radius portion at a point just short of said fluid inlet and ramp means connecting the surface of said last mentioned point and the surface at the point of maximum radius, fluid inlets through the cheek plates located to communicate with the radial inner end of said vane slots as the vanes pass successively over said ramp means to move said vanes outwardly, fluid outlet means from said chamber, one of said cheek plates being further provided with a plurality of passages therethrough communicating with the radial inner end portions of said vane slots while the vanes are passing through the working zone of said pump chamber between the fluid inlet and said point of minimum radius, conduit means leading from said plurality of passages to the pump inlet to thereby relieve the fluid pressure from being trapped beneath the vanes at the inner end of said slots to thus render the same inoperative for pumping fluid, valve means controlling communication between said passages and said conduit means, said valve means comprising a rotatable ring provided with a plurality of spaced openings therein for varying size and arranged to register with said passages of said cheek plate, the openings being of progressively increasing area so that rotation of said ring will open and increasing number of said passages in progressive succession beginning with a passage in the cheek plate at a point where the vanes are contacting the ring surface of maximum radius and thereafter opening in progressive fashion said passages throughout the balance of the pumping chamber, and means for rotating said rotatable ring to thereby vary as desired the point at which effective pumping action will begin in said pump chamber to thereby vary the delivery of said pump.
3. The subject matter of claim 1 wherein said fluid outlet means comprises radially extending passageways through said rotor from said pumping chamber inwardly toward the axis of said rotor and communicating with 5 an axially disposed passage leading to the pump outlet.
4. The subject matter of claim 1 wherein said fluid outlet means from said chamber includes valve means opening at a predetermined fluid pressure.
5. The subject matter of claim 1 wherein each vane slot in the rotor is provided with a passageway from its radially inner end leading to the intervane space ahead of the vane.
References Cited in the file of this patent UNITED STATES PATENTS Re. 23,086 Holl Feb. 22, 1949 226,773 Newcomb Apr. 20, 1880 559,324 Dyer Apr. 28, 1896 661,200 Wehinger Nov. 6, 1900 1,271,359 Price July 2, 1918 1,366,139 Traudt Jan. 18, 1921 1,482,807 Newberg Feb. 5, 1924 1,486,836 Hill Mar. 11, 1924 8 Ott Jan. 15, 1935 Sturm ..1 July 28, 1936 Curtis July 11, 1939 Kendrick Sept. 16, 1941 Kendrick Sept. 16, 1941 Tweedale Nov. 26, 1946 Ferris Jan. 16, 1951 Frank Dec. 11, 1951 Ferris Mar. 10, 1953 Baugh et a1 Mar. 17, 1953 Rathman Oct. 27, 1953 Ferris Mar. 2, 1954 Cilley Dec. 27, 1955 Rosaen Mar. 20, 1956 Nubling June 12, 1956 FOREIGN PATENTS Great Britain July 26, 1929 Great Britain Dec. 8, 1932
US530495A 1955-08-25 1955-08-25 Fluid pump Expired - Lifetime US2937599A (en)

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3106897A (en) * 1959-05-25 1963-10-15 Double A Products Company Fixed displacement variable discharge pump
US3120814A (en) * 1959-10-21 1964-02-11 Mueller Otto Variable delivery and variable pressure vane type pump
US4490100A (en) * 1981-12-29 1984-12-25 Diesel Kiki Co., Ltd. Rotary vane-type compressor with discharge passage in rotor
US4913636A (en) * 1988-10-05 1990-04-03 Vickers, Incorporated Rotary vane device with fluid pressure biased vanes
US20130183171A1 (en) * 2011-12-21 2013-07-18 Richstone Limited Rotary Cam Ring Fluid Machine
CN105874167A (en) * 2013-12-20 2016-08-17 亚历山大·M·津克 Combustion engine

Citations (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US226773A (en) * 1880-04-20 Rotary pump
US559324A (en) * 1896-04-28 I t dyer
US661200A (en) * 1899-11-21 1900-11-06 Johann Wehinger Slide-cock for mixing water and steam.
US1271359A (en) * 1916-09-20 1918-07-02 Edmund J Price Air-intake regulator.
US1366139A (en) * 1920-02-27 1921-01-18 Taber Pump Company Rotary pump
US1482807A (en) * 1921-08-31 1924-02-05 Westinghouse Electric & Mfg Co Regulator for rotary pumps and motors
US1486836A (en) * 1923-04-28 1924-03-11 Hill Compressor & Pump Company Rotary-pump pressure control
GB316670A (en) * 1928-08-02 1931-01-22 Patiag Patentverwertungsund In Rotary piston engine
GB384355A (en) * 1931-08-05 1932-12-08 Frederick Charles Greenfield Improvements in and relating to rotary machines for the compression and propulsion of
US1988213A (en) * 1931-02-12 1935-01-15 Racine Tool & Machine Company Multiple rotary pump
US2049092A (en) * 1934-07-13 1936-07-28 Sturm Erwin Rotary piston engine especially for fluid gears
US2165963A (en) * 1938-04-25 1939-07-11 Curtis Pump Co Constant flow nonpulsating pump
US2255785A (en) * 1940-09-06 1941-09-16 Manly Corp Fluid pressure device
US2256459A (en) * 1941-02-12 1941-09-16 Manly Corp Fluid pressure device
US2411602A (en) * 1942-09-03 1946-11-26 Vickers Inc Pump for power transmissions
USRE23086E (en) * 1949-02-22 Variable delivery rotary pump
US2538194A (en) * 1944-05-25 1951-01-16 Oilgear Co Hydrodynamic machine
US2578055A (en) * 1948-08-11 1951-12-11 Frank Alexander Fluid drive
US2630681A (en) * 1950-11-04 1953-03-10 Oilgear Co Rotary pump and motor hydraulic drive having a substantially constant output speed
US2631540A (en) * 1948-11-24 1953-03-17 Gen Motors Corp Rotary fluid pump
US2656972A (en) * 1949-01-31 1953-10-27 Dresser Ind Adjustable port arrangement for the high-pressure ends of fluid pumps and motors of the rotary screw type
US2670689A (en) * 1944-05-25 1954-03-02 Oilgear Co Hydrodynamic machine
US2728297A (en) * 1954-06-02 1955-12-27 Cilley Irving Variable capacity pump
US2738774A (en) * 1953-01-22 1956-03-20 New York Air Brake Co Motor
US2749843A (en) * 1953-08-13 1956-06-12 Nubling Otto Control valve for a hydraulic apparatus

Patent Citations (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE23086E (en) * 1949-02-22 Variable delivery rotary pump
US559324A (en) * 1896-04-28 I t dyer
US226773A (en) * 1880-04-20 Rotary pump
US661200A (en) * 1899-11-21 1900-11-06 Johann Wehinger Slide-cock for mixing water and steam.
US1271359A (en) * 1916-09-20 1918-07-02 Edmund J Price Air-intake regulator.
US1366139A (en) * 1920-02-27 1921-01-18 Taber Pump Company Rotary pump
US1482807A (en) * 1921-08-31 1924-02-05 Westinghouse Electric & Mfg Co Regulator for rotary pumps and motors
US1486836A (en) * 1923-04-28 1924-03-11 Hill Compressor & Pump Company Rotary-pump pressure control
GB316670A (en) * 1928-08-02 1931-01-22 Patiag Patentverwertungsund In Rotary piston engine
US1988213A (en) * 1931-02-12 1935-01-15 Racine Tool & Machine Company Multiple rotary pump
GB384355A (en) * 1931-08-05 1932-12-08 Frederick Charles Greenfield Improvements in and relating to rotary machines for the compression and propulsion of
US2049092A (en) * 1934-07-13 1936-07-28 Sturm Erwin Rotary piston engine especially for fluid gears
US2165963A (en) * 1938-04-25 1939-07-11 Curtis Pump Co Constant flow nonpulsating pump
US2255785A (en) * 1940-09-06 1941-09-16 Manly Corp Fluid pressure device
US2256459A (en) * 1941-02-12 1941-09-16 Manly Corp Fluid pressure device
US2411602A (en) * 1942-09-03 1946-11-26 Vickers Inc Pump for power transmissions
US2538194A (en) * 1944-05-25 1951-01-16 Oilgear Co Hydrodynamic machine
US2670689A (en) * 1944-05-25 1954-03-02 Oilgear Co Hydrodynamic machine
US2578055A (en) * 1948-08-11 1951-12-11 Frank Alexander Fluid drive
US2631540A (en) * 1948-11-24 1953-03-17 Gen Motors Corp Rotary fluid pump
US2656972A (en) * 1949-01-31 1953-10-27 Dresser Ind Adjustable port arrangement for the high-pressure ends of fluid pumps and motors of the rotary screw type
US2630681A (en) * 1950-11-04 1953-03-10 Oilgear Co Rotary pump and motor hydraulic drive having a substantially constant output speed
US2738774A (en) * 1953-01-22 1956-03-20 New York Air Brake Co Motor
US2749843A (en) * 1953-08-13 1956-06-12 Nubling Otto Control valve for a hydraulic apparatus
US2728297A (en) * 1954-06-02 1955-12-27 Cilley Irving Variable capacity pump

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3106897A (en) * 1959-05-25 1963-10-15 Double A Products Company Fixed displacement variable discharge pump
US3120814A (en) * 1959-10-21 1964-02-11 Mueller Otto Variable delivery and variable pressure vane type pump
US4490100A (en) * 1981-12-29 1984-12-25 Diesel Kiki Co., Ltd. Rotary vane-type compressor with discharge passage in rotor
US4913636A (en) * 1988-10-05 1990-04-03 Vickers, Incorporated Rotary vane device with fluid pressure biased vanes
US20130183171A1 (en) * 2011-12-21 2013-07-18 Richstone Limited Rotary Cam Ring Fluid Machine
US8784084B2 (en) * 2011-12-21 2014-07-22 Richstone Limited Rotary cam ring fluid machine
CN105874167A (en) * 2013-12-20 2016-08-17 亚历山大·M·津克 Combustion engine
CN105874167B (en) * 2013-12-20 2019-06-14 亚历山大·M·津克 Internal combustion engine

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