US2393223A - Hydraulic motor - Google Patents

Hydraulic motor Download PDF

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US2393223A
US2393223A US424732A US42473241A US2393223A US 2393223 A US2393223 A US 2393223A US 424732 A US424732 A US 424732A US 42473241 A US42473241 A US 42473241A US 2393223 A US2393223 A US 2393223A
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vanes
rotor
chamber
passages
vane
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US424732A
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Oscar E Rosen
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Oscar E Rosen
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03CPOSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C2/00Rotary-piston engines
    • F03C2/30Rotary-piston engines having the characteristics covered by two or more of groups F03C2/02, F03C2/08, F03C2/22, F03C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members

Description

Fan, 15, 1948., O RQSEN 2,393,223

I HYDRAULIC MOTOR Filed Dec. 29, 1941 v 3 Sheets-Sheet 1 a f WENTOR.

Jan. 15, 1946.

o. E. ROSEN 2,393,223

HYDRAULIC MOTOR Filed Dec. 29, 1941 5' Sheets-Sheet 2 INVENTOR.

o. E. ROSEN 2,393,223

HYDRAULIC MOTOR Filed Dec. 29, 1941 5 Sheets-Sheet 3 /76-/0 E w wok BY Jam, n v v Patented Jan. 15, 1946 UNITED STATES PATENT OFFICE HYDRAULIC MOTOR Oscar E. Rosen, Detroit, Mich. Application December 29, 1941, Serial No. 424,732

3 Claims.

The present invention relates to hydraulic motors and specifically to reversible hydraulic motors of the vane type.

Among the objects of the invention is to increase the efiiciency of such motors by decreasing the leakage past the vanes, particularly during the slow speed and high load conditions.

Another object is a vane type motor in which while the vanes are forced outwardly against the enclosing housing, the friction between said vanes and housing is reduced to a minimum.

Another object is a motor of the vane type which will have a greater and more uniform torque delivery than those heretofore known and used.

Still other objects will readily appear to those skilled in the art upon reference to the following description and the accompanying drawings in which Figure 1 is a central horizontal sectional view of a motor embodying the present invention.

Figure 2 is an elevational view of the inner face of member A to the left in Figure 1.

Figure 3 is a similar view of the member B to the right in Figure 1.

Figures 4 and 5 are respectively face and edge views of the rotor without the vanes.

Figure 6 is a face view of the rotor and rotor ring showing the vanes in place.

Figures 7 to 10 are face and edge views of one of the vanes somewhat enlarged; and

Figure 11 is a greatly enlarged partial sectional view showing the form of the outer edge of a vane.

A motor involving the present invention is, as shown in the drawings, composed" of two main body parts A and B which, except for details mentioned below, are quite similar, and each consists of a casting provided with cored chambers having inlet openings 2|. These openings will not ordinarily all be used, some of them being closed with suitable screw plugs. For example, the upper openings 2| in Fig. 1 may be active, while the lower ones are closed.

Each of the members A and B is provided in one face with part of the rotor chamber and the two parts are provided with suitable mating flange and seat elements 22. When the parts are together, a suitable gasket 23 will be used to prevent leakage.

Within the rotor chamber will be mounted the rotor 25 shown in detail in Figures 4 to 11, and the rotor ring 26 which is adapted to surround the rotor and coact with the rotor vanes.

maintain the shaft in its The rotor is provided with sleeve-like axial extensions 30 serving as bearing members which in turn are mounted in the parts A and B. It is also splined upon a shaft 3| which passes through the two body portions A and B having its ends projecting from the motor. The end 3| A of the shaft member is used for connection to the mechanism to be driven, while the end 3|B is preferably provided with flattened faces whereby'a handle may be applied.

The shaft 3| will be mounted in suitable antifriction bearings 32 and conventional oil rings 33 may be used to prevent escape of fluid from the rotor chamber to the outside along the walls of the shaft. Suitable end plates 34 will be used to proper position.

The faces of the two parts A and B in which the rotor chamber is formed, are shown in Figures 2 and 3, Figure 3 showing the face of part B while Figure 2 shows the part A. These faces are substantially identical and each shows the rotor end of passageways 40 and 4|, the passageways in part B being indicated as 40A and A. It should be noted that the passages 40 and 40A consist each of a number of drilled holes, the combined area of which is greater than the area of the corresponding passages 4| and 4 IA. These passageways 40 and 4|, each, 180 apart, both lead from the same chamber 20, and the passageways 40 lead into the rotor chamber near the base of the vanes, while the passageways 4| open into the chamber near the outer edge of the vanes into the arcuate depressions MB. The passageways in part B are similar to those in part A, but it should be noted that when the two parts are together, the passageways in part B are displaced degrees from those in part A. r

The rotor consists of a disc portion 45 provided with the axial bearing extension 30, and with a plurality of radial slots 46. These slots are provided in their bottoms with an enlarged chamberhave the bottom wall 48 of a purpose to be explained like portion 41 and the slot ground for later.

The rotor 45 is, as stated above, surrounded by the ring 26, which is conveniently circular on the outside, but whose inside perimeter is divided into four zones 4949A, 50- -50A. These zones have cylindrical walls and the wall of the zones 5|] and 50A are formed with a radius only slightly larger than the radius of rotor 45. The zones 49 and 49A are also cylindrical and on a like radius, but with their centers displaced from the center of which there are two of the rotor 50 that these latter zones form in effect chambers concentric with the rotor.

The two chambers are displaced from each other .180" and are of course separated by the 50A. This ring 48 is mounted in A and B, and is prefzones 5|) and the rotor chamber in parts erably maintained against movement by means member 55A and 553 having beveled edges on four sides as indicated in Figures 7 to 11. Each vane member is so beveled as to provide a small chamber 56 in the outer edge of the vane, and passages or grooves 51 in the side edges, while the bottom edge bevelling at 58 provides for passage of fluid around and under the vane in the bottom of the slot 45. It is preferred also to cut I away a portion of the bottom edge as at 59, as indicated in Figures 7 and 9.

The outer edge faces of the vane members 55A and 55B are, as shown in Figure 11, provided with a portion 80 which is ground on a radius slightly larger than the radius of the rotor and a small outer edge bevel 6 The two parts A and B are fastened together.

by suitable screws 10 with the ring 26 acting as a spacer. This leaves a small space 1| which is drained through the opening 123 leading to asuitable outlet passage in boss 13. The space I4 around shaft 3| will also be drained by a suitable passageway, "A, leading to the same boss.

Referring now to Figure 6, it will be noted that, in the embodiment shown, there are twelve vanes 55 in the rotor and that the zones 50 and 50A are of such length as to extend over three vanes while the zones 49 and 49A are somewhat longer.

It will also be seen that the depressions 4H3 form continuations of the passages 4| and MA, and that these depressions open to the spaces between the vanes several degrees behind the point where the passages 40 and 40A open to the chambers 41 behind the vanes. (This is assuming a counterclockwise rotation of the rotor, Fig. 6.)

It should also be noted that the passages 4|) and 40A are considerably larger than the passages and A.

When the several parts of the motor are assembled, the diametrically opposite passages 40 and 4| are displaced 90 from the diametrically opposite passages 40A and 4 |A so that one of each pair is in position to coact with each motor chamber or zone 49 and 49A.

The resulting action of the several parts and passages mentioned is as follows:

Fluid under pressure, supplied to a chamber 20, enters the passages 40 and 4| (to produce the counterclockwise motion, Fig. 6) and, since the passage 40 is open ahead of passage 4|, the. first action is to thrust the vane 55 outward against the ring 26. Then, as soon as the rotor has moved a few degrees, fluid from passage 4| flows behind the vane to continue the rotation.

When the rotor has moved a quarter of a revolution the fluid flows out of the passages 40A and HA into the other chamber 20 and out.

By virtue of the fact that the passage 4| is smaller than its parallel passage 40, and also the fact that passage 40 leads into a chamber'or chambers from which there is no free flow while there is free flow or its equivalent through a passage 4|," the pressure in the chambers 41 behind the vanes will be greater than the pressure between the vanes.

As a result, the vanes are held out against the ring 26 throughout what may be termed the power quadrant," that is, until the rotor hasv moved far enough for the fluid to begin to exhaust through the passages 40A and A.

- However, unless something is done to compensate for it, the outward pressure on the vanes under such conditions would be too great and would result in too great friction between the vanes and ring 26, with consequent excessive wear. So, a suitable proportion of this pressure is counteracted by forming in the outer ends of the blades the chambers 55 and connecting these with the chambers 41 by the grooves 5']. By this means the outward thrust upon the'vanes may be partially balanced and reduced to a suitable amount.

Further, by making the vanes of two leaves, the chamber 56 is maintained even when the vane is moving along the slope between, for example, zones 49 and 50.

As stated above, during the power quadrant, the vanes are pressed outwardly. When, however, the vanes reach the exhaust quadrant, the action changes. When the liquid begins to flow out, the flow will be more free through the passages 40A than through MA and consequently there will be a higher pressure between than behind the vanes, and due to the beveled edges 6|, the vanes will be thrust inwardly and will remain in their inner position until again thrust outwardly as described above.

It is, of course, to be understood that the above described action takes place simultaneously in both zones 49 and 49A, so that the motor is exactly balanced. In order to insure a balanced p.'essure, at the side edges of the vanes, the slots I40 and MI may be formed between the passages 40 and 40A and between the passages 4| and MA.

Now having described the invention and the preferred embodiment thereof, it is to be understood that the invention may be embodied in other specific forms without departing from the spirit or essential scope thereof, and it is desired that the present embodiment be considered in all respects as illustrative and not restrictive, reference being had to the appended claims rather than to the foregoing description to indicate the scope of the invention.

I claim:

1. A hydraulic motor of the vane type consisting of mating housing members having provided in their adjacent faces a. rotor chamber, fluid inlet and outlet means connected to said chamber near the periphery thereof, fluid inlet and outlet means connected to said chamber near the axis thereof, a rotor in said chamber and provided with radially movable vanes, said vanes each consisting of a pair of leaves notched at their radially inward edges to provide a small chamber, and beveled at their adjacent radially outward edges to provide a second small chamber and also provided with a passage connecting said small chambers, said last mentioned fluid inlet entering said chamber at the inner edges of said vanes, means for supplying fluid under pressure to an inlet at the periphery and an inlet near the axis and means for maintaining a higher pressure at the second mentioned inlet than that at the peripheral inlet,

slot, an inlet chamber for receiving fluid under and their adjacent side edge corners whereby to and means for conducting the higher pressure riphery oi. said rotor between the outer edges of fluid to the outer edge faces 01' said vanes. said vanes.

,2. In a rotary vane type motor, a rotor having 3. In a rotary motor of the vane type, a rotor radial slots therein, movable vanes in said slots, provided with radial slots, and with movable vanes said vanes being each provided with a chamber 5 in said slots, said vanes each consisting of two in its radially outer edge and with conduit means leaves arranged in face to face relation, the leaves connecting said recess with the inner end 01' its being beveled on their adjacent outer edge corners pressure, a relatively large passageway leading form a chamber in said outer edge and channels from said inlet chamber to said rotor to the inner 10 leading therefrom to the rearward edge face. ends 01' said slots, and a relatively small passage- OSCAR E. ROSEN. way leading from said chamber to the outer pe-

US424732A 1941-12-29 1941-12-29 Hydraulic motor Expired - Lifetime US2393223A (en)

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Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2521997A (en) * 1946-12-06 1950-09-12 Oscar E Rosaen Vane type hydraulic motor
US2544988A (en) * 1949-03-12 1951-03-13 Vickers Inc Power transmission
US2544987A (en) * 1947-01-04 1951-03-13 Vickers Inc Power transmission
US2588430A (en) * 1945-10-15 1952-03-11 Odin Corp Rotary blade pump
US2636481A (en) * 1949-05-28 1953-04-28 New York Air Brake Co Vane type hydraulic motor
US2653551A (en) * 1947-12-22 1953-09-29 New York Air Brake Co Fluid pump
US2743897A (en) * 1952-11-28 1956-05-01 Lynn T Elliott Unitary power operator for opening and closing valves
US2760348A (en) * 1952-08-05 1956-08-28 Wetmore Hodges Motor-compressor in plural temperature refrigerating system
US2765750A (en) * 1954-03-09 1956-10-09 Hartmann Mfg Company Fluid pump or motor
US2826179A (en) * 1954-08-02 1958-03-11 Airway Products Inc Hydraulic motor
US2832199A (en) * 1953-04-30 1958-04-29 American Brake Shoe Co Vane pump
US2856861A (en) * 1955-09-09 1958-10-21 American Brake Shoe Co Vane for use in a rotary fluid apparatus
US2960075A (en) * 1957-09-20 1960-11-15 Hazel B Phillips Rotary type fluid motor
US3000324A (en) * 1958-10-06 1961-09-19 Rosaen Filter Co Vane for rotary pumps
US3086475A (en) * 1963-04-23 rosa en
US3112709A (en) * 1961-07-14 1963-12-03 Coal Industry Patents Ltd Vaned pumps and motors
US3119345A (en) * 1962-05-24 1964-01-28 Hypro Engineering Inc End ported roller pump
US3120154A (en) * 1960-12-01 1964-02-04 Lafayette E Gilreath Hydraulic motor
US3255704A (en) * 1965-02-24 1966-06-14 New York Air Brake Co Pump
US3468074A (en) * 1966-08-25 1969-09-23 Theodore B Eddy Rotatable fixture and expanding mandrel
JPS4937770B1 (en) * 1970-09-09 1974-10-12
WO2007007415A1 (en) * 2005-07-14 2007-01-18 Mayekawa Mfg. Co., Ltd Water-hydraulic vane motor, food processing cutter driven by the motor, and food processing cutting facility
US20090110577A1 (en) * 2004-11-19 2009-04-30 H.P.E. High Performance Engeneering S.R.I. Variable delivery vane oil pump, in particular for oil

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3086475A (en) * 1963-04-23 rosa en
US2588430A (en) * 1945-10-15 1952-03-11 Odin Corp Rotary blade pump
US2521997A (en) * 1946-12-06 1950-09-12 Oscar E Rosaen Vane type hydraulic motor
US2544987A (en) * 1947-01-04 1951-03-13 Vickers Inc Power transmission
US2653551A (en) * 1947-12-22 1953-09-29 New York Air Brake Co Fluid pump
US2544988A (en) * 1949-03-12 1951-03-13 Vickers Inc Power transmission
US2636481A (en) * 1949-05-28 1953-04-28 New York Air Brake Co Vane type hydraulic motor
US2760348A (en) * 1952-08-05 1956-08-28 Wetmore Hodges Motor-compressor in plural temperature refrigerating system
US2743897A (en) * 1952-11-28 1956-05-01 Lynn T Elliott Unitary power operator for opening and closing valves
US2832199A (en) * 1953-04-30 1958-04-29 American Brake Shoe Co Vane pump
US2765750A (en) * 1954-03-09 1956-10-09 Hartmann Mfg Company Fluid pump or motor
US2826179A (en) * 1954-08-02 1958-03-11 Airway Products Inc Hydraulic motor
US2856861A (en) * 1955-09-09 1958-10-21 American Brake Shoe Co Vane for use in a rotary fluid apparatus
US2960075A (en) * 1957-09-20 1960-11-15 Hazel B Phillips Rotary type fluid motor
US3000324A (en) * 1958-10-06 1961-09-19 Rosaen Filter Co Vane for rotary pumps
US3120154A (en) * 1960-12-01 1964-02-04 Lafayette E Gilreath Hydraulic motor
US3112709A (en) * 1961-07-14 1963-12-03 Coal Industry Patents Ltd Vaned pumps and motors
US3119345A (en) * 1962-05-24 1964-01-28 Hypro Engineering Inc End ported roller pump
US3255704A (en) * 1965-02-24 1966-06-14 New York Air Brake Co Pump
US3468074A (en) * 1966-08-25 1969-09-23 Theodore B Eddy Rotatable fixture and expanding mandrel
JPS4937770B1 (en) * 1970-09-09 1974-10-12
US20090110577A1 (en) * 2004-11-19 2009-04-30 H.P.E. High Performance Engeneering S.R.I. Variable delivery vane oil pump, in particular for oil
US7866963B2 (en) * 2004-11-19 2011-01-11 H.P.E. High Performance Engeneering S.R.L. Variable delivery vane oil pump, in particular for oil
WO2007007415A1 (en) * 2005-07-14 2007-01-18 Mayekawa Mfg. Co., Ltd Water-hydraulic vane motor, food processing cutter driven by the motor, and food processing cutting facility
JPWO2007007415A1 (en) * 2005-07-14 2009-01-29 株式会社前川製作所 Vane type hydraulic motor, cutting machine for food processing driven by the motor, and cutting device for food processing

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