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Publication numberUS2983226 A
Publication typeGrant
Publication dateMay 9, 1961
Filing dateJan 16, 1953
Priority dateJan 16, 1953
Publication numberUS 2983226 A, US 2983226A, US-A-2983226, US2983226 A, US2983226A
InventorsLivermore William T
Original AssigneeLivermore William T
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Injection filled liquid pump
US 2983226 A
Abstract  available in
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Claims  available in
Description  (OCR text may contain errors)

y 1961 w. T. LIVERMORE 2,983,226

INJECTION FILLED LIQUID PUMP Filed Jan. 16, 1953 flu 04 1904 IC APP/5' RH 705 IN V EN T 0R.

W/ZZ/AM 7: A Vii/14 0/?5' U ti d statssPaifl,"

INJECTION FILLED LIQUID PUMP William T. Liver-more, Grosse Pointe Farms, Mich. (509 Middle River Drive, Fort Lauderdale, Fla.)

Filed Jan. 16, 1953, Ser. No. 331,567

3 Claims. (Cl. 103-42) the pump is run at high speed, that cavitation may result from incomplete filling of pumping elements at the intake side of the pump when atmospheric pressure alone is depended upon to produce such filling. Such cavitation may result in noisy operation of the pump as well as inefiiciency and undue wear of the elements.

In accordance with the present invention, at least a substantial portion of the delivered fluid is caused to flow directly back into the intake chamber of the pump, preferably through a jet nozzle or aperture which feeds such fluid under a high velocity directly to the pumping elements at the intake chamber, instead of passing all of the delivered fluid to the sump as in conventional practice. Such injection filling has been found in practice to assure complete filling of the pumping elements, substantially eliminate cavitation, and produce exceptionally quiet and eflicient operation.

When the pump is run at very high speeds, the centrifugal force imparted to the liquid moved by impellers at the intake chamber produce a considerable force, tending to throw the fluid radially outwardly before the impeller reaches the sealing edge of the pumping intake chamber and thus produces a considerable tendency toward cavitation. By injecting hydraulic fluid at high speed tangentially, or at a slight angle to the tangent of the rotor, the work required to speed the intake fluid up to rotor speed is eliminated or substantially reduced, a smoother fiow into the working chamber with minimized turbulence is elfected, and/or a substantial pressure in the immediate area of the cut-off edge of the intake chamber may be created to resist the centrifugal forces tending to produce cavitation.

Accordingly, it is the principal object of the present invention to provide a simple and effective means of assuring complete filling of the pumping elements at the intake chamber to an extent not permitted by reliance on total intake supplied from sump at atmospheric pressure.

Another object is to use direct return of at least a substantial portion of the discharge of the pump to the intake chamber per se instead of to the sump.

Another object is to return such discharge under a velocity and in a direction which will assist the filling of the pumping elements, either through imparting at least a portion of the required rotor velocity to the liquid moving into the pump impeller chambers, or in building an effective super atmospheric pressure head in the final area of intake fluid engagement by the pump impellers.

Another object is to provide a tangential jet feed for such directly returned liquid in the direction of impeller movement at the inlet chamber.

Another object is to provide means for directing a limited portion of the pumprdischarge to the sump to provide necessary cooling in cases Where continuous direct recirculation would result in undue heating of the hydraulic fluid.

These and other objects will be apparent from the following detailed description of a typical embodiment and from an examination of the drawing thereof.

The drawing comprises a sectional elevation of a slipper type rotary pump incorporating provision for injection filling in a schematically shown recirculating hydraulic system.

Referring to the drawing, it will be seen that a pump rotor 10 is adapted to rotate in a counterclockwise direction within a pump housing 11, driving slipper impellers 12 through an eccentric arc in the housing to provide pumping action between an inlet chamber 13 and an outlet chamber 14 in the housing. Hydraulic pressure from an outlet port 15 is delivered to outlet passage 16 supplying hydraulic apparatus from which the hydraulic fluid is exhausted to a sump S. Hydraulic fluid delivered in excess of apparatus requirements also communicates through passage 17 with a by-pass valve 18 which may operate as a pressure regulator and safety valve controlled by the strength of the spring 19.

After fluid pressure is built up to overcome the spring, the bypass valve is opened and the surplus discharge from the pump is directed through the passage 20 and nozzle 21 directly to the intake chamber 13 of the pump.

Such directly returned fluid is preferably delivered under velocity in the general direction of the peripheral movement of the slippers passing throughthe intake chamber and may be tangential to the rotor. Such velocity delivery of fluid directly to the rotors avoids at least part of the necessity for acceleration of the fluid in filling the expanded slipper chambers in the intake are, thereby assisting smooth flow into such chambers and minimizing the possibility of turbulence and cavitation. It will also be seen that fluid delivered under velocity into the intake chamber 13 may build up an effective pressure head in any portion of the intake chamber where the form is such as to reduce velocity. This pressure can be utilized to overcome centrifugal effects of high speed operation which might otherwise prevent the hydraulic fluid from completely filling the slipper chambers.

While it is preferred to deliver the fluid under velocity in the direction of perimeter travel, it will be understood that at least a substantial portion of the benefit of direct return may be obtained through the development of an effective superatmospheric pressure head in the intake chamber. For example, if the nozzle 21 were to direct fluid toward the rotor in a radial rather than tangential direction, such velocity might be utilized to build up an elfective pressure head which would materially assist in avoiding cavitation even though such velocity injection did not directly impart required acceleration to the fluid in the direction of impeller travel.

It is important, however, that whatever direction the velocity injection takes relative to the rotor, it must be so arranged as to prevent interference with low pressure flow from the sump. Thus, in the present embodiment, the intake 22 from sump S is arranged to enter laterally at the side of the nozzle 21 when the velocity is high and pressure therefore is at a minimum so that velocity flow from the nozzle, which may be made high by making the nozzle small, will not oppose flow from the sump Patented May 9,1961.

delivery, it may be desirable to lead a portion ofthe sur-' plus delivery to the sump, as by an orifice 23 and passage 24, to any extent necessary to avoid overheating of the fluid through direct recirculation. On the other hand, where the flow to the hydraulic apparatus is continuous and comprises a relatively large portion of the total out-' put of the pump, it may be desirable to direct a portion of the fluid returned from the hydraulic apparatus directly to the velocity injector, as by an optional passage 25 under a partial pressure headmaintained by orifice 26 rather than passing it all to sump through return:

passage 27.

While a particular embodiment has been described above in detail, it will be understood that numerous modifications may be resorted towithin the scope of my invention as defined in the following claims.

1. In a recirculating hydraulic pressure system, a rotary positive displacement hydraulic pump having a pump rotor and an inlet and an outlet communicating with said rotor, a reservoir for storing hydraulic fluid connected to said inlet, and means for minimizing cavitation in the filling of the pump during the intake cycle of operation, said means being characterized 'by fluid passage means for recirculating a portion of the pump out put back to the inlet without passing through said reservoir, said passage means directing fluid toward said inlet and including a restricted discharge opening to provide a jet action at a velocity exceeding the inlet flow from said reservoir and in a direction substantially tangential to the perimeter of the pump rotor thereby efiectively supercharging the inlet of said pump. 1

2. In a hydraulic pressure system, a rotary positive displacement hydraulic pump having a pump rotor communicating with an outlet adapted to discharge hydraulic fluid for meeting hydraulic pressure requirements and an inlet. for receiving hydraulic fluid passing through said pump, a reservoir connected to said inlet for supplying said pump with hydraulic fluid, and a branch hydraulic circuit between the outlet and inlet of said pump terminating in a restricted discharge opening directed substantially tangential to the perimeter of said rotor to assist the filling of said pump through jet action at a velocity exceeding the inlet flow from said reservoir and effective to supercharge the inlet of said pump.

3. In a recirculating hydraulic pressure system having a reservoir and hydraulic pressure actuated apparatus discharging into said reservoir, a positive displacement rotary pump having a pump rotor with fluid impeller elements and an inlet and an :outlet communicating with said rotor, a by-pass valve connected to said outlet for venting a portion of the discharge of said pump, and means for minimizing cavitation in the filling of the pump in advance of said impeller elements during the intake cycle of operation characterized by fluid passage means for delivering at least a portion of by-passed discharge directly to said inlet without passing through said reservoir, said passage means including a restricted discharge opening to provide a jet action at a velocity exceeding the inlet flow from said reservoir directing fluid to said inlet in a direction. generally'tangential to the path of said impeller. element in said intake cycle of operation thereby elfectively supercharging the inlet of said. pump.

References Cited in the file of this patent UNITED STATES PATENTS 1,112,158 Pedersen Sept. 29, 1914 1,350,095 Eddison Aug. 17, 1920 1,969,881 Gardner Aug. 14, 1934 2,056,994 'Woods Oct. 13, 1936 2,216,053 Staley Sept. 24, 1940 2,251,664 Davis -I. Aug. 5, 1941 2,268,807 Curtis 2 i r r Jan. 6, 1942 2,325,931 Avigdor Aug. 3, 1943 2,363,528 Hulman et a1. Nov. 28, 1944 2,446,730 Wemp l Aug. 10, 1948 2,466,812 Jacobsen Apr. 12, 1949 2,589,067 Erickson Mar. 11, 1952 2,612,112 Williams Sept. 30, 1952 2,724,335 Eames Y "Nov. 22, 1955 2,733,662 Hunter Feb. 7, 1956 2,746,392 Klessig et al. May 22, 1956 2,748,711 Drude June 5, 1956 FOREIGN PATENTS 476,440 France May 11, 1915 559,108 Great Britain Feb. 4, 1944

Patent Citations
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US2268807 *Mar 8, 1941Jan 6, 1942Curtis Pump CoAircraft fuel pump
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Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US3054262 *Apr 18, 1961Sep 18, 1962Ford Motor CoIntegrated hydraulic system
US3065708 *Oct 12, 1959Nov 27, 1962Mechanisms CompanyFluid pressure transducer
US3066608 *Nov 22, 1960Dec 4, 1962Livermore William TMultiple ported transmission pump
US3097546 *Aug 29, 1960Jul 16, 1963 Transmission mechanism
US3139905 *Sep 11, 1961Jul 7, 1964Rosaen Nils OFluid superchargers
US3198121 *Sep 26, 1962Aug 3, 1965Syncroflo IncTankless water pressure system
US3199771 *Oct 16, 1962Aug 10, 1965Becker G M B H GebMulticell machine operating as a combination pressure-vacuum generator
US3322134 *Feb 11, 1964May 30, 1967Danfoss Ved Ing M ClausenPressure-regulating valve
US3614266 *Dec 24, 1969Oct 19, 1971Ford Motor CoCompact positive displacement pump
US3620646 *Jul 1, 1970Nov 16, 1971Gen Motors CorpCentral hydraulic system for a vehicle
US3645647 *Jan 14, 1970Feb 29, 1972Ford Motor CoPositive displacement fluid pumps
US4013174 *Oct 22, 1975Mar 22, 1977The Manitowoc Company, Inc.Swing drive with automatic shut-down control
US4014198 *Jan 12, 1976Mar 29, 1977Langenstein & Schemann AktiengesellschaftDrive mechanism of a pair of forging or stretching rollers
US4213744 *Mar 3, 1978Jul 22, 1980Eaton CorporationHydraulic pump and improved by-pass flow means therefor
US4310289 *Nov 15, 1979Jan 12, 1982Zahnradfabrik Friedrichshafen, Ag.Hydraulically operated steering system with pressure control
US5083907 *May 25, 1990Jan 28, 1992Eaton CorporationRoots-type blower with improved inlet
US6328538 *Aug 13, 1999Dec 11, 2001John J. RademacherIntegrated fuel pump
DE3418384A1 *May 17, 1984Nov 21, 1985Peter Graf Von IngelheimDevices for speed-independent delivery regulation combined with energy recovery in constant-delivery pumps - especially in lubricating-oil pumps
DE4138516A1 *Nov 23, 1991May 27, 1993Luk Fahrzeug HydraulikPumpe
DE102009015990A1 *Apr 2, 2009Jul 8, 2010Audi AgVane cell pump, particularly fuel pump or lube oil pump, for supplying liquid medium in internal combustion engine of motor vehicle, has suction face, pressure side and recirculation line that is guided from pressure side
DE102012100702A1 *Jan 30, 2012Aug 1, 2013Zf Lenksysteme GmbhPump e.g. roller vane pump for supplying fluid to power steering of motor vehicle, has return port that is opened tangentially in annular suction channel
EP0763659A2 *Aug 30, 1996Mar 19, 1997LUK FAHRZEUG-HYDRAULIK GmbH & Co. KGVane pump
Classifications
U.S. Classification417/79, 417/310, 60/468, 60/469, 60/430
International ClassificationF04C15/00, F04C15/06
Cooperative ClassificationF04C15/062
European ClassificationF04C15/06B