US2691349A - Rotary pump - Google Patents

Rotary pump Download PDF

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US2691349A
US2691349A US24179551A US2691349A US 2691349 A US2691349 A US 2691349A US 24179551 A US24179551 A US 24179551A US 2691349 A US2691349 A US 2691349A
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Prior art keywords
ball
shaft
socket
pump
rotor
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Ernest A Cuny
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Ernest A Cuny
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    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04POSITIVE DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04CROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C3/00Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type
    • F04C3/06Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees

Description

Oct. 12, 1954 E. A. CUNY 2,691,349

ROTARY PUMP Filed Aug. 14, 1951 2 Sheets-Sheet l INVENTOR. fk/v'sr/ ['wvy BY y ya 30 7'70 Oct. 12, 1954 E. A. CUNY 2,691,349

ROTARY PUMP Filed Aug. 14, 1951 2 Sheets-Sheet 2 INVENTOR. Zws7 (b vy Patented Oct. 12,1954

UNITED STATES PATENT OFFICE ROTARY PUMP Ernest A. Cuny, New York, N. Y. v Application August 14, 1951, Serial No. 241,795

4 Claims.

The invention herein disclosed relates to rotary pumps of the type disclosed in Patent No. 2,242,- 058 of Ma 13, 1941, in which displacement is effected by cooperatively related, bladed and slotted rotors operating on intersecting axes within an enclosed housing.

Objects of the present invention are to improve the operating efficiency of such devices, to simplify construction and to reduce production costs.

Particularly it is a purpose of the invention to join the cooperating rotor elements in a selfcentering ball and socket form of universal joint.

A further special object of the invention is to provide a rotary pump of the character indicated which will be self-adjusting in respect to pressure and thereby adapted to deliver fluid under substantially constant pressure.

Other desirable objects attained by the invention are set forth or will appear in the course of the following specification.

The drawings accompanying and forming part of the specification illustrate certain present commercial embodiments of the invention. Structure, however, may be modified and changed as regards the immediate disclosure, all within the true intent and broad scope of the invention as hereinafter defined and claimed.

Fig. 1 in the drawings is a broken cross sectional view of one of the pumps; Fig. 1a is a broken sectional detail of the universal joint.

Figs. 2 and 3 are broken face views of the companion inlet and outlet sections of the pump casing;

Fig. 4 is a sectional view of the upper portion of the pump casing on substantially the plane of line 4-4 of Fig. 1, showing the cross connection of the inlet and outlet passages;

Fig. 5 is an enlarged broken sectional detail of the mid-portion of the pump casing, on substantially the plane of line 55 of Fig. 2;

Fig. 6 is a face view of the slotted disc rotor;

Fig. 7 is a broken detail view showing how the rounded edges of the slotted rotor fit in rolling engagement with the blades of the other rotor;

Fig. 8 is a sectional view of a modified form of the invention in which volum is automatically controlled according to pressure;

Fig. 9 is a broken and part sectional end view of this form of the pump;

Fig. 10 is a sectional view as on substantially the plane of line Ill-I 0 of Fig. 8;

Fig. 11 is a broken part sectional view of the segmental form of bladed rotor shaped for universal joint engagement over the ball center of the slotted rotor.

Figs 1 and 8 illustrate the arrangement of the posite sides of the disc and at diametrically opposite points of the pump casing.

The pump casing is shown made up of two sections 22, 23, secured together in fiat, face-to-face engagement by screws 2t.

The section 22 has an inlet 25 opening into an arcuate channel 26 partly surrounding the pump chamber l8 and opening into this inlet portion of the pump chamber by an arcuate slot 21.

At a point almost diametrically opposite the intake 25 the arcuate channel 26- terminates in a cross-over port 28 registering with a corresponding port 29 in the face of the other housing section 23, the latter port being open to the arcuate inlet channel 3!] which opens through segmental port 32 into the diagonally opposite intake portion of the pump chamber, as will b clear from Fig. 4.

At a diametrically opposite portion of the pump chamber an arcuate slot 33 places the pump chamber in communication with a surrounding arcuate discharge channel 38 in section 23, terminating in a port 35 in register with port 36 of casing section 22, which latter port communicates with arcuate channel 31 in communication with the diagonally opposite discharge portion of the pump chamber through an arcuate slot 38, Fig. 4.

The slots 21 and 32, as shown in Fig. 4, are displaced laterally or transversely of the pump axis to locate them to the intake portions at opposite sides of the slotted disc rotor l9 and similarly, the slots 33 and 38 are offset to the discharge portions of the pump chamber at diagonally opposite sides of the disc rotor.

Consequently the volumetric displacement at opposite sides of the angularly or inclinedly related rotors is fully utilized and pressure is substantially balanced at opposite sides of the rotors.

The arcuate or segmental inlet and outlet slots substantially balance transverse pressure on the rotors, leaving them free to operate with low frictional losses.

The two rotor shafts are shown connected by double ball and socket joints.

In Fig. 1 the shaft l5 carries an inner ball element 39 having a socket receiving the transverse roll member 40 on the end of the shaft I6, forming a universal joint drive connection. The shaft I6 is tapered t fit a correspondingly tapered socket in the outer ball and socket element 4| of the shaft l6, being secured in this relation by I nut 53.

Shaft l5 also carries an outer ball and socket element 42 journaled in the housing section 22 and receiving the ball portion of the outer ball and socket element 4| of shaft 16.

The outerball and socket element 42 of shaft l5 which, in effect, constitutes the bladed rotor l1, may be made up as shown in Fig. 11, with the socket forming portions of the blades 2i in separate segments 43 which can be secured over the ball portion 41 of the other shaft by screws 44.

In the construction shown in Fig. 8 the inner ball and socket connection indicated at 40 in Fig. 1, is omitted, the ball member 39 of shaft [5 engaging within the ball and socket member 4! of shaft [6 and the latter fitting within the ball and socket element 42 of shaft I5.

The shafts may have a fixed angular relation as shown in Fig. 1, where said shafts are journaled in fixed, angularly related bearings 45, 46, or the angular relationship may be adjustable as for variable displacement or pressure control purposes.

Figs. 8 and 9 show the second shaft, l6, journaled at 41 in rectangular bearing box 48 slidably guided in a parallel-sided bearing housing 49.

A spring 50 is adiustably mounted at 51 in this bearing housing, tensioned against the sliding bearing block 41 to hold it in the position of maximum shaft angularity and hence in the position of maximum pump displacement.

With increase of pressure developed in the pump chamber against the slotted disc rotor, the spring will be compressed, yielding, under sufficient pressure, possibly to the position of zero displacement, with shaft It in line with shaft 15.

By proper selection and setting of spring 50, the pump may be made self-controlling for pressure or displacement.

This self-controlling feature renders the pump particularly desirable for such uses as rocket fuel pumps.

While described as a pump, it will be realized that the rotary displacement machine disclosed may have many other uses and the present disclosure will be so understood.

Fig. '7 shows in detail how the slots may be cut in the disc forming rotor 19 on curved lines 52 so as to make easy rolling engagement with the sides of the blades 2|.

The universal joint connection 39, 40, Figs. 1 and in, may be set so as to maintain a running clearance between the edges of the blades and the edges of the slots. To facilitate such setting the shaft 16 carrying the cross roll of the universal joint may be tapered and be secured by the nut 53, Fig. l, in a taper seat in the hearing sleeve portion 54 which carries shaft IS.

The various parts of the pump may be cast, 'molded or otherwise formed in ferrous or nonferrous metals or in hard plastic or hard rubber, enabling the pump to be made for handling different kinds of fluids.

Additional advantages are that the machine is reversible and is suited to operation at varying rates ranging from low to high speed operation.

What is claimed is:

l. The rotary machine herein disclosed com- 4 prising companion bladed and slotted disc rotors rotating on intersecting axes with the blades of the first rotor in the slots of their disc rotor. shafts carrying said rotors, a ball and socket member at the end of one of said shafts and a ball and socket member at the end of the other of said shafts, the ball and socket member of one shaft receiving the ball and socket member of the other shaft and said first shaft having a ball member fitting within the socket portion of the ball and socket member of said other shaft.

2. The rotary machine herein disclosed comprising companion bladed and slotted disc rotors rotating on intersecting axes with the blades of the first rotor in the slots of the disc rotor, shafts carrying said rotors, a ball and socket member at the end of one of said shafts and a ball and socket member at the end of the other of said shafts, the ball and socket member of one shaft receiving the ball and socket member of the other shaft and said first shaft having a ball member fitting within the socket portion of the ball and socket member of said other shaft, and said ball and socket member of the first shaft constituting the bladed rotor and the socket portion of said ball and socket member being made in ball socket blade forming segments.

3. The rotary machine herein disclosed comprising companion bladed and slotted disc rotors rotating on intersecting axes with the blades of the first rotor in the slots of the disc rotor, shafts carrying said rotors, a ball and socket member at th end of one of said shafts and a ball and socket member at the end of the other of said shafts, the ball and socket member of one shaft receiving the ball and socket member of the other shaft and said first shaft having a ball member fitting within the socket portion of the ball and socket member of said other shaft, and a universal joint drive connection between said ball member and the end of said other shaft.

4;. The rotary machine herein disclosed comprising companion bladed and slotted disc rotors rotating on intersecting axes with the blades of the first rotor in the slots of the disc rotor, shafts carrying said rotors, a ball and socket member at the end of one of said shafts and a ball and socket member at the end of the other of said shafts, the ball and socket member of one shaft receiving the ball and socket member of the other shaft and said first shaft having a ball member fitting within the socket portion of the ball and socket member of said other shaft, a bearing for one of said shafts adjustable transversely of the shaft axis and means for variably positioning said adjustable bearing.

References Cited in the file of this patent UNITED STATES PATENTS Number Name Date 2,101,051 Cuny 1. Dec. 7, 193"! 2,242,058 Cuny May 13, 1941 2,353,780 Neuland July 18, 1944 2,475,096 Holl July 5, 1949 FOREIGN PATENTS Number Country Date 26,930 Great Britain 1913 557,673 Great Britain Nov. 30, 1943

US2691349A 1951-08-14 1951-08-14 Rotary pump Expired - Lifetime US2691349A (en)

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Cited By (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2908224A (en) * 1954-08-20 1959-10-13 John W Houser Variable delivery pressure fluid engine
US3044409A (en) * 1957-07-09 1962-07-17 Lee T Harris Variable displacement hydraulic assembly
US3095708A (en) * 1957-07-09 1963-07-02 Lee T Harris Variable displacement hydraulic assembly
US3101059A (en) * 1959-06-30 1963-08-20 Elmer W Easter Fluid pump or motor
US3101700A (en) * 1960-06-14 1963-08-27 Meredith E Bowdish Rotary compressor or engine
US3487787A (en) * 1967-12-06 1970-01-06 Thompson Wendell L Vane type rotary fluid displacement device
US3769944A (en) * 1972-05-08 1973-11-06 Redskin Eng Co Rotary engine
US3993417A (en) * 1975-02-24 1976-11-23 Harrington Walter J Rotary apparatus with axially movable vanes
FR2411320A1 (en) * 1977-12-08 1979-07-06 Rovac Corp Compressor-pressure regulator
US4354807A (en) * 1977-12-08 1982-10-19 The Rovac Corporation Compressor-expander of the vane type having canted vane cavity
FR2716501A1 (en) * 1994-02-24 1995-08-25 Ksb Ag axial piston pump oblique control plate having side rooms in which the fluid passes.

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191326930A (en) * 1912-12-02 1914-07-16 Cfcmug Improvements in or relating to Rotary Pumps and Motors.
US2101051A (en) * 1935-07-20 1937-12-07 Cunward Inc Rotary fluid displacement device
US2242058A (en) * 1937-11-05 1941-05-13 Ernest A Cuny Rotary fluid displacement device
GB557673A (en) * 1942-11-12 1943-11-30 Kevitt Rotherham Rotary vane-type blowers or the like
US2353780A (en) * 1941-09-20 1944-07-18 Alfons H Neuland Fluid pump and motor
US2475096A (en) * 1945-10-09 1949-07-05 James W F Holl Beveled interengaging impellers supercharger or blower

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB191326930A (en) * 1912-12-02 1914-07-16 Cfcmug Improvements in or relating to Rotary Pumps and Motors.
US2101051A (en) * 1935-07-20 1937-12-07 Cunward Inc Rotary fluid displacement device
US2242058A (en) * 1937-11-05 1941-05-13 Ernest A Cuny Rotary fluid displacement device
US2353780A (en) * 1941-09-20 1944-07-18 Alfons H Neuland Fluid pump and motor
GB557673A (en) * 1942-11-12 1943-11-30 Kevitt Rotherham Rotary vane-type blowers or the like
US2475096A (en) * 1945-10-09 1949-07-05 James W F Holl Beveled interengaging impellers supercharger or blower

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2908224A (en) * 1954-08-20 1959-10-13 John W Houser Variable delivery pressure fluid engine
US3044409A (en) * 1957-07-09 1962-07-17 Lee T Harris Variable displacement hydraulic assembly
US3095708A (en) * 1957-07-09 1963-07-02 Lee T Harris Variable displacement hydraulic assembly
US3101059A (en) * 1959-06-30 1963-08-20 Elmer W Easter Fluid pump or motor
US3101700A (en) * 1960-06-14 1963-08-27 Meredith E Bowdish Rotary compressor or engine
US3487787A (en) * 1967-12-06 1970-01-06 Thompson Wendell L Vane type rotary fluid displacement device
US3769944A (en) * 1972-05-08 1973-11-06 Redskin Eng Co Rotary engine
US3993417A (en) * 1975-02-24 1976-11-23 Harrington Walter J Rotary apparatus with axially movable vanes
FR2411320A1 (en) * 1977-12-08 1979-07-06 Rovac Corp Compressor-pressure regulator
US4354807A (en) * 1977-12-08 1982-10-19 The Rovac Corporation Compressor-expander of the vane type having canted vane cavity
FR2716501A1 (en) * 1994-02-24 1995-08-25 Ksb Ag axial piston pump oblique control plate having side rooms in which the fluid passes.
DE4405945A1 (en) * 1994-02-24 1995-08-31 Klein Schanzlin & Becker Ag Pump, with inclined plate and axial pistons,
US5531576A (en) * 1994-02-24 1996-07-02 Ksb Aktiengesellschaft Wobble plate pump with side chambers through which fluid flows
DE4405945C2 (en) * 1994-02-24 1998-07-09 Klein Schanzlin & Becker Ag Swash plate pump with flow-through side chambers

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