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Publication numberUS1927799 A
Publication typeGrant
Publication dateSep 19, 1933
Filing dateMar 7, 1932
Priority dateMar 7, 1932
Publication numberUS 1927799 A, US 1927799A, US-A-1927799, US1927799 A, US1927799A
InventorsJohn Mann
Original AssigneeGoulds Pumps
Export CitationBiBTeX, EndNote, RefMan
External Links: USPTO, USPTO Assignment, Espacenet
Rotary pump
US 1927799 A
Abstract  available in
Images(3)
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Claims  available in
Description  (OCR text may contain errors)

J. MANN y ROTARY PUMP Sept. 19, 1933.

3 sheets-sheet 1 Filed March 7, 1.932

f SEQ 4 -.llll .I3

Sept. 1'9, 1933. '.J. MANN 1,927,799

ROTARY PUMP Filed March '7, i932 s sheets-sheet 2 /33 INVENTUR WITNESS www Sept. 19,- 1933. .1.A MANN ROTARY PUMP Filedjlarch '7, 1932 .3 Sheets-Sheet 3 QWy varies with the square of space in spaces as, Atween the teeth or Patented 19; 1933 UNITED STATES Goulds Pumps,

John Mann, Seneca Falls, N.' Yt, assignor to Inc., Seneca Falls,

corporation of NewYork. nppucau'onmwh'v, 1932. sei-m1 No. 591,232 r e claims. (oplos-s) This invention relates to certain new and useful improvements in rotary pumps.

Most all rotary pumps usually take the liquid into the rotating element against the opposing centrifugal force set up by the gears, cams, pistons orv blades. As this force the `velocity of the outer part of the cam, gear or blade, it limits the rotative speed of the pump to such a speed that centrifugal force does not entirely prevent lling of part of the tooth spaces. Atmospheric pressure only is available to bring liquid into the suction openings of the pump, and when the rim speed of the gears or blades is high enough to create a centrifugal force equal to the pressure of atmosphere, little or no ow can take place into the suction openings'of the rotary pump. This limits the speed at which these pumps can operate, necessitating comparatively low revolutions per minute of the gear or rotor, the operating speed dependingupon the diameter of the gears or blades used, so that the resulting centrifugal force does not entirely prevent the iilling of the spaces between the teeth'of. gear or rotor.

vvOperation of these gear pumps at suiilciently reduced speeds will lower the centrifugal force to such value that the pump tooth spaces will partially ll, but this reduces the volume pumped to less than would be possible if the tooth spaces could ll entirely. y

The spaces between the teeth which are receding from the'suction opening are `only partially iilled with liquid, and at the bottom of the tooth spaces a' condition of partial vacuum exists.

When these teeth reach the discharge `cham` ber, the pressure existing at this point quickly forces the liquid back into the unfilled spaces, and this sudden filling of the pockets occurs with a distinct impact, giving a noisy condition of op'- eration, increases wear and sets up shocks which are carried through both the pump andpiping.

TheJ operation of rotary pumps of the sliding blade type or the piston type is much the same in effect, as with rotary pumps of the gear type.

The main object of the present invention is to provide means of overcoming the centrifugal force set up by the teeth of the gear o'rv the sliding blade or the piston, orrotor of the rotary type of pump which tends'to prevent filling of the inlet for instance, the spaces be- 'cams of the pump, causing a reduction from the maximum possiblev displacement of thev rotary pump and limiting the rotarotation of the y Figure 5.

tion to a piston type rotary pump.

tive speeds at which they can be effectively operated. y l

Other objects and advantages relate to the details of the structure and the form and relation of the parts thereof, all as will more fully appear from the following description taken in connection with the accompanying drawings, in which: Figure. l'is an elevation of a rotary. pump of this invention using an internal ring gear with idler pinion.

Figure 2 is an e 2 2, Figure 1.

Figure 3 is a section taken on line -3-'3, Figure 2.

Figure 4 isv ure 2.

arged section taken on line a section taken on line l-4:, Fig-V 7o is a section taken on line 5-5v Figure 2.

Figure 6 is a section similar to Figure 2 of a modified form of pump using spur or mangle type gears. l y r v Figure '7 is a section taken on line 'l-.'l, Figure 6.' 4 l Figure 8 is a section taken 'on line 8-8, Figure 0.

Figure 9 is a section taken on line 9 9, Fig- -ure 10 illustrating the application of my inven- Figure 10 is a section taken on line Figure 9. i

Figure'll is a section taken on line 11-11, Figure 12 illustrating the application of lmy invention to a sliding blade type of rotary pump.

Figure 12 is a section 'taken'on line 12'12, Figure 11.

The self-contained combination lconstituting the present invention is much the` same in gen' eral organization, relation and effect regardless of the type of-rotary pump -involved and for instance; whether the I pinion type of pump is used or whether the 'spur or mangle type gear rotary piston or sliding blade pump vis used in vthat in all these types the rota-'J tion of the 'gearapistonsor blades builds up` a ce of centrifugal force which the liquid, preventing en opposes the en ire filling of the suction spaces of the rotor resulting in a liquid displace-I l in increased internal ring gearwith idler 95 a noisy operating conthe operation of this invention as applied tothe the latter of which has one side closed by a closure section 4 secured to the section 1 in any suitable manner, as by bolts 5.

Thisclosurey section 4 may carry the usual crescent 6 disposed between a portion of the internal gear and the idler pinion. The chamber 3 is preferably of substantially cylindrical form and constitutes the pump chamber of the gear elusive differs only inthose points essential to pump, whereas the chamber 2 is preferably of involute form and constitutes the pump chamber of a centrifugal pump.

The inlet for fluid leads through passageway 7 to the chamber 2 and the outlet from chamber 2 leads through the passageway 8 to the inlet 3' of the chamber 3, the outlet from chamber 3 being illustrated at 38.

For thepurpose of supplying fluid to the inlet 3 of the gear pump ata pressure corresponding substantially with the centrifugal force built up by the gears of the pump there is provided a cylindrical rotor 9 journaled in the wall of the casing 1 which separates the chambers 2 and 3. On the side of the rotor facing the chamber 2 it is provided with a series of blades 10 which may be spirally arranged, and as shown are three (3) in number, and may be integrally formed with the rotor and are positioned in the chamber 2 for rotation therein.

On the opposite face of the rotor 9 adjacent the chamber 3 there are provided a series of Aspaced teeth 11 constituting an internal gear Asubstantially fitting the chamber 2` for rotation therein. The idler pinion 12 may be mounted eccentrically on stub shaft 13 projecting inwardly from the closure section 4 for free rotation thereon.

In order to drive the rotor 9 with its blade elements 10 it is mounted .centrally upon a shaft 14l extending outwardly through bearing 15 mounted in boss 17 formed on casing l.

Any suitable packed joint'or bearing may be provided for preventing leakage of fluid around shaft 14, as for instance packing' 18 backed by sleeve 19 surrounding shaft 14 and pressed against the packing as by means .of spring 20 interposed between a shoulder on sleeve 19, and the base of a cap 21 threaded on boss 17.

, With this arrangement it will be-apparent that ftwo pumps including rotor elements are mounted` in a single casing and that the rotor elements are of substantially equal diameters and are driven at the same speed by avsingle shaft so that the iiuid passes from the centrifugal pumping chamber 2 to the gear pump including chamber 3 under substantially the same pressure as the centrifugal force developed by the gear pump so that the fluid is free to enter the inlet 3 of the gear pump under atmospheric pressure.

'Ihe structure shown in Figures 6 to 8 inadopt the combination to a rotary pump using spur or mangle type gears.

In the construction here illustrated by those figures the pump casing is formed of two sections 22 and 23 secured together in any suitable manner, as by bolts 24. In this construction the involute chamber 25 of the centrifugal pump is formed in the casing 23 and the oval chamber in the wall 26 and. in the casing section 22 and passes through the chamber 42 of the gear pump and the gear 29 is mounted thereon, preferably for rotation therewith. A second shaft 30 is jour- 'naled in the wall 26 and in the casing 22 in substantial p'arallelism with the shaft 27' and has the.

gear 31 mounted thereon for rotation therewith and for meshing engagement with the gear 29.

Asthe'shaft 30 is the driving shaft it extends outwardly through boss '32 on casing section 22 in the same manner as shaft 14 extends outwardly through boss 17 and may have the same packing construction. Further, shaft 30 projects through the wall 26 of casing section 23 and has mounted thereon an impeller 33 of the centrifugal type and which may include any number of blades 34, as for instance, three, which may be spirally arranged on the face of the impeller disk for rotation within the involute chamber 25.

An inlet fitting 35 is provided and secured to the section 23- in any suitable manner as by bolts 36. Liquid is supplied through this inlet to the rotor of the centrifugal pump consisting of the impeller 33 in the involute chamber 25. Liquid is forced by the pump through the outlet 37 from chamber 25 and through conduit illustrated in dotted lines, Figures 6 and 7, to the inlet 39 of the gear pump under the same condition of equalized pressure with the centrifugal force developed by the gear pump as existed withA the tion of Figures 1 to 5.

Fluid is forced outwardly. from the chamber 42 as through outlet 40.

construc- Thev piston or `plunger type of rotary pump as illustrated in Figures` 9 and 10 comprises a cylindrical casing 45 having an inlet 46 and'outlet 47 for fluid. A rotor 48 is concentrically mounted in the chamber and,l asshown, fits tightly within two diametrically opposed sections of the casing periphery as indicated.. at 49 and 50. Drive shaft 51 extends through the wallof the casing and is connected tol the rotor 48 in any suitable manner for driving the same. This rotor, in the usual way, is formed with diametrically extending slots or passageways therethrough extendng at right angles to each other as indicated at 52. v

Within these passageways are mounted separate sliding pistons 80 of somewhat lesser length than the diameter of the rotor so that they are capable of sliding within the rotor into and out of substantial Contact` with the interior wall of the casing. This sliding movement is effected by connecting the pistons to the respective crank arms 53 and 54 as by pins, 55 and 56, and these crank arms are mounted on a stub shaft 57 secured in the wall of the Icasing 45 as, -for instance, by nut 5.8, and as this stub shaft is mounted eccentrically with respect `to the drive shaft 51 for the rotor, rotation of the rotor carrying the crank arms andy 'pistons about the stub shaft 57 will cause a reciprocation of the pistons in a manner well known.

Combined 'with this type of pump, the feature of this invention resides in the provision of a centrifugal pumping chamber 59 formed within the casing 45, and as shown, the rotor 48 is provided on one of its exterior faces with a plurality of vanes or impeller blades `60 which may be arranged spirally upon the face of the rotor 51 in its rotary movement not only actuates the rotary I pumping apparatus, but simultaneously rotates the' impeller vanes.

The outlet 61 from chamber 59 is connected as by a conduit with the inlet 46 of the rotary pump so that fluid is supplied to said inlet under pressure. With this construction, it will be apparent that the speed ofrotation of the rotor is equal to the speed of rotation of the centrifugal pumping device including the impeller blades 60.

In Figures 1l and .12, this invention is shown as applied to a sliding blade type of rotary pump. As illustrated, this pump comprises a casing 71 whichv may be formed in sections if desired-secured together in any suitable manner.

A slotted rotor 72 is eccentrically mounted within the casing 71 so that its periphery will contact with the inner wall of the casing at one lline. A suitable blade or lblades '73 is or are slidably mounted in the slot which extends through the rotor. As suggested, this blade may be a single integral blade or the blade may be formed in two t sections as illustrated, or any number of blades may be providedeither integral or sectional. It is perhaps preferable to form the inner surface or rotor containing. chamber within casing Z1 in the shape of the'well known limaon curve so that the ends of the blade or blades will always remain in contact with the interior surface of the chamber.

In this applicationof my invention, the eccentric rotor is driven by a shaftr'M extending through the wallof the casing and connected to' the rotor in anysuitable manner, and with this construction in like manner as the construction shown in Figures 9 and 10, one end 'surface of the rotor is provided with a plurality of vanes or impellerblades 75 positioned in the centrifugal pumping chamber 76- formed within the casing. The outlet from the centrifugal pumping chamber 76 leads through passageway '77 to the inlet '78 of the rotary pump.

An outlet '79 is illustrated leading from the rotary pump chamber while fluid is supplied to the rotary .pump in saidv chamber under the pressure developed by operation of the centrifugal pumping device described. f-

From al consideration of the above, it will be apparent that the'disadvantages inherent in the operation of a so-called rotary pump are elimilnated in-that the uid is supplied to the suction side of the pump under a vpressure substantially equal to the centrifugalforce developed by the pumping element or elements of the rotary pump. Howeverysubstantial advantages in the operation of such a pump are obtained when the liquid is applied to the v,suction side of the rotary pump under pressures which may be somewhat less or somewhat greater than the centrifugal force developed by operation of the pump.

Further, it will beapparent'that the pumping apparatus herein illustrated and described is of a unitarynature in whichy the driving element v ofthe rotary pump and the impeller of the centrifugal pump are simultaneously rotated by the same means and at the' same speed, although variations in this respect are possible.

And although I have shown and described specific constructions of pumping apparatus as constituting illustrative embodiments oflmy ina casing having two chambers ventina, I do' not desire' to restrict myself to the details of form,` construction or arrangement, as various changes and modification may be made without departing from the scope of the appended claims.

I claim: l

1. In a pumping apparatus, the combination of therein, of a rotor journaled in the wall 'between said chambers and provided with impeller blades on onesurface in one of said chambers and gear elements on the opposite surface inthe 'other chamber, and means for driving said rotor.

2. In a pumping apparatus the combination of a casing having two chambers therein of a rotor journaled in the wall between said chambers andprovided with impeller blades on one surface in one of said chambers, and gear ele-f ments on the opposite surface in the other cham-.- ber, means for drivingsaidrotor, and means connecting the outlet from the chamber including theimpeller elements with the inlet to the vided with impeller blades on one surface in one of said chambers, and gear elements on the opposite surface inY the other chamber.

4. In a pumping apparatus, the combination of a casing having two chambers therein, of a shaft journaled in said casing, a rotor positioned between said chambers and mounted on the shaft to bedriven by said shaft, said rotor being pro-l vvided with impeller blades on one surface in one of said chambers,v gear elements on the opposite surface in theother chamber, and means connecting the outlet from onel of said chambers with the inlet to the other chamber.

5. In a pumping apparatus, the combination with a casing having two chambers therein, of l a shaft journaled in said casing, a rotor positioned between said chambers and .mounted on the shaft to be driven by said shaft, saidrotor being provided with impeller blades on one surface in one of said chambers, and a rotary type of pump mounted on the. opposite side inftheother chamber, said rotary pump having 'the driven element thereof mounted vtov revolve'about 'a fixed axis eccentricv to the axis of rotation of said rotor. I

6. In a pumping apparatus,

a shaft Journaled'in said casing, a' rotor posithe combination, with a casing having two chambers therein, of

tioned between said chambers and mounted on pump mounted on the opposite side in theother axis eccentric to the Aaxis/gf rotation of said rotor, and means connecting the outlet lfrom the the shaft to` be driven by said shaft, said rotor being provided with impeller blades -on one surface in one of said chambers, a rotary type of chamber includingthe impeller blades'with vthe inlet te the chamber containing said rotary pump.

JOHN; l

fisc

Referenced by
Citing PatentFiling datePublication dateApplicantTitle
US2440624 *Mar 16, 1944Apr 27, 1948Wemp Ernest ELiquid handling means
US2451055 *May 9, 1944Oct 12, 1948Edward Beacham ThomasFuel pump
US2492075 *Oct 30, 1945Dec 20, 1949Kinney Mfg CompanyVacuum pump
US2500227 *Jan 18, 1946Mar 14, 1950Nash Engineering CoLiquid pumping unit
US2500228 *Mar 30, 1946Mar 14, 1950Adams Harold EPump assembly
US2513446 *May 17, 1946Jul 4, 1950Brown And BrownPump or motor
US2547392 *Apr 2, 1946Apr 3, 1951Hill Francis AContinuous contact internal rotor for engines
US2592476 *Feb 7, 1948Apr 8, 1952Laval Steam Turbine CoSeries arrangement of positive and nonpositive screw pumps
US2601397 *Apr 11, 1950Jun 24, 1952Francis Hill MyronRotary fluid displacement device
US2607296 *May 16, 1946Aug 19, 1952Herman G MuellerFluid pump unit
US2679211 *Nov 24, 1948May 25, 1954Hjordis NaessVariable output pump
US2688925 *Sep 27, 1950Sep 14, 1954Thompson Prod IncMixed flow multiple pump
US2774578 *Sep 24, 1952Dec 18, 1956Nat Dairy Res Lab IncMethods and apparatus for whipping food products
US2823518 *Nov 19, 1953Feb 18, 1958Thompson Prod IncAircraft fuel pumping system
US2971691 *Aug 13, 1956Feb 14, 1961Heraeus Gmbh W CPumping system
US3016017 *Aug 21, 1959Jan 9, 1962Brakeshoe International S ARotary pumps and motors
US3016834 *Oct 7, 1957Jan 16, 1962Eaton Mfg CoRotary pumps
US3119339 *Nov 12, 1958Jan 28, 1964Clarke Built LtdAerating apparatus
US3128708 *Dec 19, 1960Apr 14, 1964New York Air Brake CoPump
US3202101 *Jul 5, 1963Aug 24, 1965American Brake Shoe CoMethod and means for preventing cavitation in hydraulic piston and vane pumps
US3635602 *Sep 17, 1970Jan 18, 1972Chandler Evans IncLifting tip seal pump
US3640646 *Mar 26, 1970Feb 8, 1972Ingersoll Rand CoAir compressor system
US4624627 *Feb 22, 1985Nov 25, 1986Tunks Larry MSelf-priming pump
US4642030 *Nov 25, 1985Feb 10, 1987Robert Bosch GmbhArrangement for feeding fuel from supply tank
US4755110 *Jul 17, 1987Jul 5, 1988Hoerbiger Ventilwerke AktiengesellschaftPiston-type compressor
US4787826 *May 22, 1987Nov 29, 1988Karl Schnell Gmbh & Co. MaschinenfabrikPump, particularly for highly viscous materials
US4797068 *Jun 5, 1987Jan 10, 1989Hitachi, Ltd.Vacuum evacuation system
US4808078 *Oct 5, 1987Feb 28, 1989Phoenix Park SystemsPump control system for instantly reversing the drive motor
US4822251 *Feb 29, 1988Apr 18, 1989Leybold AktiengesellschaftVacuum pump having an rpm-measuring device
US5257913 *Apr 5, 1991Nov 2, 1993Schwarzer Prazision Jurgen Schwarzer Gmbh & Co. KgHand tool for producing local over or under pressure
US5261796 *Nov 27, 1992Nov 16, 1993Vickers, IncorporatedElectric-motor in-line integrated hydraulic pump
DE1170787B *Jan 28, 1959May 21, 1964Gasturbinenbau Und EnergiemascZahnradpumpe hoher Drehzahl
DE3500139A1 *Jan 4, 1985Jul 10, 1986Bosch Gmbh RobertAggregat zum foerdern von kraftstoff aus einem vorratstank zu einer brennkraftmaschine
DE3743261A1 *Dec 19, 1987Jun 29, 1989Kloeckner Humboldt Deutz AgTwin pump for a flow medium with different delivery rates and delivery pressures
DE3812109A1 *Apr 12, 1988Oct 26, 1989Schwarzwaelder Uhrwerke FabrikDetergent-feeding device for domestic appliances, in particular dishwashers
WO2016022193A1 *May 20, 2015Feb 11, 2016Imo Industries, Inc.Dual integrated organic working fluid pump
Classifications
U.S. Classification417/203, 91/493
International ClassificationF04C15/00, F04B23/08, F04D9/00, F04C11/00, F04D9/04, F04B23/00
Cooperative ClassificationF04C11/005, F04D9/041, F04C15/0042, F04B23/08
European ClassificationF04C15/00C, F04D9/04B, F04C11/00C, F04B23/08