US1876833A - Pump - Google Patents

Description

Sept. 13, 1932. lE, BENEDEK 1,876,833

K PUMP Filed Jang. 28, 1931 4 Sheets-Sheet 2 grt/vento@ Sept. 13, 1932. E. BENEDEK 1,876,833

PUMP Filed Jan. 28, 19:51 4 Sheets-sheet 2 atto: we

Sept. 13, 1932. Ef BENEDEK 1,87-65833 led Jan. 28. 1931 4 Sheets-Sheet 5 Sept. 13, 1932.' A E, BENEDEK 1,876,833

A PUMP.

Filed Jan. 28. 1931 4 Sheets-Sheet 4 ELE-K 5min..

annual,

Patented Sept. 13, 1932 UNITED STATES lnlvraNr omer.

ELEK BENEDEK, 0F IILWAUXEE, WISCONSIN, ASSIGNOR T0 THE HYDRAULIC PRESS IAYNUFACTUBINGYCOIPANY, 0F IOUNT GILEAD, OHIO FUI? Application nea January as, 11131.- seriai no. 511,684.

.This invention relates to rotary multiple plston pumps. Pumps of the type to which the present invention applies include a cylinder barrel rotatable about a pintle and containing a series of radial cylinder bores each of which communicates alternately with inlet and outlet passages in the pintle, together with a series of pistons reciprocating in said bores vand driven by a surrounding impeller which V.rotates with the cylinder barrel. In pumps of the type referred to each piston 1s connected to the impeller through a load transmitting T-shaped structure freely reciprocable in the impeller in a direction normal to the axis of reciprocation of its connected piston; and, as heretofore constructed, each T- shaped structure bore against a set of antifrlction' rollers provided in the impeller to sustain the transmitted piston load and to insure freedom of reciprocation of the T- shaped structure.

One object of the present invention is to maintain an effective oil lilm between each T- shaped structure and impeller capable of sustaining the heavy loads involved and to thus provide and maintain a substantially frictionless bearing therebetween, to thereby ,make possible the elimination of the sets of anti-friction rollers heretofore required.

Another object is to insure an ample supply of lubricant to the coacting 'surfaces` o the T-shaped structures and impeller.

Another object is to provide a positive, double-acting, driving connection between each T-shaped structure and its coacting piston, which will afford suiicient flexibility to permit self-alignment of each piston in its coacting bore, and which at the same time will insure against eccentric loadingof the piston under all conditions of operation.

Another object of the invention is to provide a novel construction and cooperative arrangement'of pintle and cylinder barrel in which the pintle is supported at its respective ends in the pump casing and the relatively long cylinder barrel, which surrounds and has oil film bearing on the intervening portion of the pintle, has anti-friction bearthereto. A pintle ing at its ends alone on the pintle adjacent the secured ends thereof and 1s of very rigid non-'yielding construction to adapt it for centrally supporting, and for `overcoming ten-- on a larger scale, taken substantially along Fig. 4 is an end view of the pintle and end support. Y l F'Fig. 5 is a sectional view on the line 5-5 of Fig. 6 is an enlargeddetail view of one of the bearing blocks shownin Fig'. 3.

Fig. 7 yis a horizontal sectionalview, partly in elevation, of a modified form of pump embodying the .present inventlon.

Fig. Sis a sectional view on the line 8-8 v f of Fig. 7.

The pump shown in Figs. 1 to 6 is enclosed within an appropriate housing 10 having a pair of end heads 11 removably secured 12, extended through the housing, constitutes a support for an inner rotary member or cylinder barrel 13 and also contains -two pairs of passages 14 and 15 through which liquid is supphed to and discharged from the' pump. A close running fit is provided between the cylinder barrel and pintle, the cylinder barrel being sup- A ported primarily by a pair of anti-friction bearings 16 mounted on the pintle.

The pintle is rigidly but adjustably sup-yported at its opposlte ends in a pair of slide blocks 17 guidedbetween pairs of horizontal flanges 18 preferably formed integral with the end heads 11 of the housing. The slide b1ocks.17 are simultaneously actuated and controlled through appropriate means such as a frame 19 having links 20 connected to the respective blocks (see Fig. 2). An adjustng screw 21, journalled 1n the housing and threaded through a boss 22 on the frame 19, serves to actuate and control the frame and to thereb advance or retract the pintle 12 and thus shift the axis of rotation of the cylinder barrel 13. v

Each pair of pintle passages 14 and 15 extends lengthwise of the pintle from an intermediate portion to the end thereof, each of the upper passages x14 communicating with a pair of ports 23, and each of the lower passages communicating with a pair of ports 24. AThe cylinder barrel contains four -sets of radial bores 25, the bores of each-set having end ports 26 which communicate alternately with an upper port 23 and lower port 24 in the pintle during rotation of the cylinder barrel about the pintle. Each bore 25 contains a hollow piston 27 which is actuated by an outer rotary member or impeller 28 through connections which will be later described. The impeller 28 is in the form of a cylindiical drum secured to and supported by end disks 29. The end disks are 'provided with central hub portions 30 journalled in surrounding anti-friction bearings 31 fixed within circular flanges 32 formed in the end heads 11. The impeller 28 is driven by a air of pinions 33 which mesh with teeth 34 ormed upon the periphery of the end disks 29, the pinions being ixed'to a drive shaft 35 journalled in the end heads 11.

Each piston 27 is connected to the impeller 28 through 'a T-shaped structure comprising a shank 36 rigidly connected to and projecting inwardly froma cross-head 37 of plate like form. Each cross-head 37 extends at right angles to its connected shank 36 and is guided within a slot 38 formed in the impeller substantially tangential to the inner periphery thereof.

The shank 36 projects into its associated piston 27 and is provided at its inner end with a ball 39 which is snugly fitted within the piston and bears centrally against the base thereof, the ball being positively retained in. this position by a sleeve 40 screwed into the outer open end 4of the piston and bearing against the ball. A key 41 prevents y accidental displacement of the sleeve 40 and a key 42, loosely engaged with the cross-head 37 and with the sleeve 40, prevents rotation of the sleeve and piston with respect to the cross-head and shank.

It will be noted that the internal diameter of the sleeve 40 is slightly greater than that of the shank 36, so that the piston 27 and sleeve are permitted some freedom of movement about the ball .39 sucient to permit self-alignment of each piston within its coacting bore. The freedom of the crosshead permitted by the ball 39 'should not be confused as an operative freedom. The ball above explained the piston is never eccentrically loaded. Furthermore the positive confinement of the ball between the base of the piston andthe end of -the sleeve insures a positive mechanical connection between the shank 36 and a piston in both directions of reciprocation, thereby affording a positive suction stroke as well as a positive pressure stroke of the piston.

The load on each piston 27 is sustained by a reaction face on the outer rotary member in the present instance comprising the inner side of a stationary reaction plate 43 removably xed in a slot 44 formed in the impeller adjacent and parallel to one of the cross-head guide slots 38. i Each reaction plate is retained in place in a well known manner by a screw 45 in a transverse locking plate 46 and each reaction plate is provided with means interposed between the plate and the associated cross head for carrying the hydraulic piston load. Whether the interposed bear-j ing means is connected to the reaction plate or-the associated cross head is not fundamentally important. It is important in accordance with the invention that the bearing means comprise a substantially plane faced bearing element, but the number of elements ,interposed between each reaction plate and the associated cross head is not critical, andthere may be one or more such elements for carrying the hydraulic load oneach piston. In this instance each reaction plate is slotted to receive a plurality of spaced stationary bearing blocks 47 which project slightly beyond the inner face of the reaction plate. As indicated in the illustrative embodiment shown particularly in Fig. 6, the exposed face of each block 47 is slightly inclined in opposite directions, lengthwise of the reaction plate, from a central, transversely extending high portion 48, but it will be understood that the advantages resulting from my iinproved organization of load transmitting means maybe obtained without the bearing blocks having inclined faces as shown. The space between each cross-head 37 and its coacting reaction plate 43 is ilooded with lubricant in a manner to belater described. It will be understoodthat the reaction plates preferably are separable and removable for convenience in machining an assembly, but

.that it is not necessary in obtaining the advantages of the invention thatv thereaction faces be formed on separate parts. f

The arrangement is such that, during lengthwise reciprocation of each cross-head 37, lubricant is draggedthereby into the thin substantially frictionless bcaringis provided between each cross-head andi'ts coacting reaction plate. It will beundestoodthat in practice when itis desired' tousofa plurality of bearing blocks having inclined faces the degree of inclination ofzthefacc's' 49is quite illimite, the inclination portrayed-in Fig. 6

being greatly cx.aggerated merely to facilitate illustration.

It will "be observed that '.tl1e1pintl e-12is rigidly mounted at its ends-inA the-blocks 17 and that the cylinder barrelv-llia's al-second..

ary oil film bearing throughout{substantially its whole length on thepintlebut has its main bearing on anti-friction bearings' 16 one of which is provided adjacent each rigidly supported end of the pintle. lj Thfe' cylinder barrel is relatively Ylongand, is heavy and rigid or non-yielding infits construction and thus actsas a central snpportlfoi.tlie portion of the pi ntle intermediate its'rigidlymounted y ends. By this construction andarrang'ement the strains occasioned'by thehydraulic action incident to operation of the pump are not permitted to deflect'or distortthe 'pintle.

In thepump shown the'zspace between the cylinder barrel 13 and impellei' drum 28 is utilized as a reservoir for lubricating oil, and for that purpose an oil retainer cover 50 is applied to the 'external periphery oftheV impeller, andthe supporting end Vdisks 29 are 'closely fitted to the ends of the cylinder barrel, as indicated in Figs. 1 and 2. Suiiicient oil is maintained in this space to flood all of he slots 38 and ,44 and other'spaces within the impeller, during rotation of the cylinder barrel and impeller, so that an ample supply' of lubricant to the-cross-heads 37 and bearing blocks 47 is assured. `It will be noted that leakage of oil past the several pistons'27 from the bores 25 discharges directly into this space between the cylinder barrel and Vimpeller to at least partially compensatefo'r oil leakage therefrom. Y

In the pump shown in Figs. 1 lto 6 the impeller drum 28 rotates about a. fixedaxis coincident withy the centers ofthe bearings 31 and is driven at high speed from the shaft 35 through the pinions 33. The cylinder barrel 13 rotates about an adjustable'axis coincident with the axis of the adjustable pintle 12, rotation being imparted togthe cylinder barrel from the impeller through the pistons and the T-shaped structures hereinabove described. By adjustment of the pintle through the control screw 21 andA frame 19 the axis of rotation of the cylinder barrel may be made to coincide with that of the impeller, in which position pump displacement is zero, or it may be shifted tov one side or the other of the axis of rotation of the impeller to thereby cause the pump to discharge in one direction or the other at a rrate dependent upon the de- .grce of eccentricity of the cylinder'barr'el with respect to the impeller.

In pumps of this general'type the pintle is ordinarily lubricated by oil which escapes from the several cylinder ports 26, during the pressure stroke of each of the several pisvtons 27, and which spreads to form a film over irregular areas between the pintle and cylinder barrel,'but during the suction stroke of each piston the negative pressure in the ports 26 tends to destroy the oil film thus produced causing wear between the Vpintle and cylinder barrel. To eliminate this difli- -culty small pressure reservoirs are provided for supplying oil to the pintle during the suction strokes of the piston. Reservoirs for this purpose are shown at 51. Each is in the form of a bore, closed at one end by a plug, 52, and open at the other end to a channel 53 which surrounds the pintle. B efore putting the pump into use these bores 51 and channels 53 are filled with oil. Then during operation pressure is built up therein by oil i* which escapes from the ports 26 during'the pressure strokes of the pistons and finds its way along` the pintle intothe channels 53,.' This pressure-isfthen avaliable to force oil along 'the pintle and thus maintain an oil film thereon during the suction stroke of the It will be noted that the outer rotary' member 28 isprovidedlwith a plurality of pairs of opposed faces lnormal tothe respective piston and cylinder assembly axes, the outer of which faces constitute reaction faces and the inner of which faces coloperate 'with the cross heads 37 for moving the latter and connected assemblies outwardly during the suc- Y tion strokes.

llu

The pump shown in Figs. 7 and 8 is similar in many respects to that hereinabove described. It is enclosed within a housing 10 having removable end heads 11. In this instance however thecylinder barrel 13 is supported in bearings Eidg-supported by circular flanges 55in theendheads 11 for rotation about a fixed axis. The pintle 12 does not support the cylinderbarrel but is centered therein by anti-friction bearings 56 therebetween, one end lofthe pintle being loosely fitted in a hub -57 formed integral with one of the end heads 11. A key 58 holds the pintle against rotation. The' pintle is provided with the usual-discharge and return passages 14 and 15 and with ports 23 which cooperate with the cylinder ports 26 in the usual manner, during rotation of the cylinder barrel thereabout.

Invthis instance the cylinder barrel is driven b a'shaft 59 journaled in one of the end hea s 11 and having a flanged end 60 fixed to the cylinder barrel.

The impeller 28 is(supported upon antifriction bearings 31 carrled by a ring 61, supported for lateral displacement between the end heads 11'. A trunnion 62 projecting from one side of the ring is guided within a boss 63 formed on the housing 10', and a screw 64 journaled in the diametrically opposite side of the ring is threaded within a boss 65 formed in the housing. The arrangement is such that by rotating the screw 64 the ring 61 and impeller may be shifted in one direction or the other with respect to the cylinder barrel to thereby reverse or vary the displacement 0f the pump in a well known manner.

The several pistons 27 are connected to the impeller 28 in exactly the same manner as hereinabove described.

Although both machines shown have b ee referred to as pumps, through the foregoing description, either will function, with out modification, as a hydraulic motor.

Various changes may be made in either of the pumps hereinabove specifically described without departing from or sacrificing the advantages of the invention as defined in the appended claims.

I claim 1. In apump or motor the combination of a pntle, a radial series of reciprocable piston and cylinder Y assemblies rotatable about said pintle, a rotary member surrounding said assemblies and rotatable therewith,

Va. cross-head connected with each of said assemblies and freely reciprocable with respect to said rotary member in a direction normal to the axis of reciprocation ofthe connected assembly, and a lubricated bearing 'block interposed between each of said crossheads and said rotary member for sustaining the thrusts of said assemblies, each of said blocks having a pair of substantially plane faced bearing surfaces oppositely inclined in. the direction of reciprocation of its associated cross-head. I

2. InY a pump or motor the combination of a pntle, a radial series of reciprocable piston and c lnder assemblies rotatable about said pint e, a rotary member surrounding said assemblies and rotatable therewith,l a

cross-head connected with each of said assemblies and guided for reciprocation in said rotary member in a direction normal to the axis of reciprocation of the connected assembly, and means in said rotary member providing a plurality of bearing elements formed with oppositely inclined substantially plane faced lubricating bearing surfaces engaging each of said cross-heads and slightly inclined in the directions of reciprocation thereof.

3. In a pump or motor the combination of a pntle, a radial series` of reciprocable piston and cylinder assemblies rotatable about said pntle, a rotary member surrounding said assemblies and rotatable therewith, a cross-head connected with each of said assemblies and guided for reciprocation in said rotary member in a direction normal to the axis of reciprocation of the connected assem- I of a pntle, a radial series of reciprocable pis- ,ton and cylinder assembliesmotatable about said pntle, avrotary member comprising an oil retaining drum surrounding said assemblies and rotatable therewith, a cross-head connected with each of said assemblies and reciprocable in said drum in a direction normal to the axis of reciprocation of the connected assembly, and a set of bearing blocks carried by said drum and interposed between each of said cross-heads 4and saiddrum for sustaining the thrusts of said assemblies, said blocks having substantially plane faced bearing surfaces lubricated by oil contained in said drum.

5. In a pump or motor the combination bly but no operative rocking freedom andy adapted to form a rigid and positive driving connection between each shank and piston, a rotary element rotatable with said cylinder barrel, and a cross-head rigidly connected with each shank and guided for reciprocation in said rotary element in a direction normal to the axis of reciprocation of the aociated piston.

6. In a pump or motor the combination of a housing, a pntle, a separate support for each end of said pintle slidably mounted in said housing, a cylinder barrel rotatable on said pintle and having a plurality of c linder bores therein, a piston reciprocab e in each bore, a rotary element, bearings fixed .in said housing for supporting the opposite` ends of said rotary'element, a cross-head connected with each piston and guided forreciprocation in the rotary element in a direction normal to the axis of reciprocation of the connected piston, and means for simultaneously shifting said pintle sup orts to thereby shift the axis of` rotation o said cylinder barrel with respect to that of said rotary ele-V ment.

7. In a pump ormotor the combination of a housing, a' pintle supportedat-,both ends in said'housing', a long nonyielding cylinder barrel having rotativeIV lubricant filmbearing on saidV pintle throughout sub-` stantially the length of the pintle intermediate its end bearings, a plurality of sets ofbarrel rotatable on said pintle, cylinder bores formed in said barrel having ports cooperating with said pintle ports, pistons reciprocable in said b ores, a channel encircling said pintle and offset from saidpintle ports, and a pressure chamber in said cylinder barrel communicating with said channel. y

,9. In a pump or motor the combination of a pintle, a cylinder barrel rotatable about said pintle and having a plurality of radial cylinder bores therein, a hollow piston reciprocable in each bore and having a solid inner end for acting onfluid in the bore, a shank projecting into cach piston, a ball'at the end of each shank centrally confined within each piston, a retainer sleeve coacting with each ball within which said shank is afforded freedom permitting crosshead alignment during assembly but no operative rockingfreedom and adapted to form a positive driving connection between each shank and piston, a rotary element rotatable with said cylinder barrel, and a crosshead .rigidly connected with each shank and guided for reciprocation in said rotary element in a direction normal to the'axis of reciprocation of the associated piston.

10. In a pump or motor, the combination of a casing, a pintle having rigid supporting bearing at its respective ends in said casing, a long rigid nonyielding cylinder barrel extending substantially the length of the pintle intermediate its bearings and having main rotative bearing on said pintle in bearings motor lthe combination of provided therefor adjacent the pintle bearin and secondary lubricant film bearin on sald pintle throughout the length thereo intermediate said main bearings, said cylinder barrel also having a plurality of cylinder bores therein, pistons reciprocable in the bores, and means to impart reciprocation to said pistons.

11. In a pump or motor the combination of a casing, a pintle having rigid supporting bearing at itsv respective ends in saidcasing and inlet and outlet passages therein, portsl in said pintle communicating respectlvely withsaid passages, la long rigid nonyielding cylinder barrel extending substantially the .length of the pintles intermediate its bear.-v

ings and having main rotative bearing on said pintle in bearings provided therefor adj acent the pintle'bearings and secondary lubri-` cant film bearing of said vpintle throughout the length thereof intermediate said main bearings, said cylinder barrel also having a plurality of cylinder bores therein and ports cooperating with said pintle ports, pistons re-V ciprocable inthe bores, and means to impart .reciprocationto said pistons. Y

12. In a pump or. motor the combination of a housing, .a pintle having inlet and outlet vvalve openings therein, a rigid cylinder barrel lhaving pintle distortion preventing and rotative oil film bearing on said pintleand having a plurality of cylinder bores therein communicating with the valve openings, a

rotary element surrounding the cylinder barrel and rotatable with said barrel about an individual axis, means affording cooperative engagement between the pistons and the ro- Y tary element, and means for bringing` about a relative shifting movement between the barrel and rotary element axes alongastraight line so related to the valve openings that thev correlation vof valve openings and barrel bores never varies regardless of the relative positions of the barrel and rotary element axes.

13. In a pump or motor, inner and outer rotary members rotatable about individual axes, radially disposed piston and cylinder assemblies connecting the elementsV for rotation together, said outer memberk having reaction faces, cross heads connectedl to the pistons and being mountedl for reciprocation with respect tov said reaction faces, substan 'tially plane faced bearing blocks interposed betweensaid reaction faces and said cross heads and being carried by one and slidably 'engaging the other, and means for retaining within said outer rotaryv element a body of lubricant constantly in contact with the slid# i ing crossheads and subject ito compression by centrifugal force according to the speed of rotation of said rotary members, said lubricant being unaifected by the o erating Vpressure changes in the working uid employed.. in said pump or motor.

14. In a pump or motor, innerv and outer rotary'members rotatable about individual axes, radially disposed piston and cylinder assemblies connecting the members for rotation together and including crossheads slidal bly engaging the outer rotary member, and

means for retaining within said .outer rotary member the hydraulic medium leaking past the pistons whereby to provide a body' of lubricant constantly in contact with the l0 sliding crossheads and subject to compression by centrifugal force according' to the speed of rotation of said rotary members, said lubricant being unaffected by the operating pressure changesin the hydraulic agent u employed in said pump or motor, said outer element having tangential grooveways therein for reciprocably receiving the crossheads, andsaid crossheads having their outer faces engaging and coacting with bearing portions 9 on said outer rotary member slightly inclined in the directions of reciprocation of said cross heads whereby to provide high pressure oil film bearings for said crossheads which increase in efficiency as the speed of rotation u of said rotary elements increases.'

15. In ahydraulic pump or motor, the combination of a pintle, a radial series of reciprocable piston and cylinder assemblies rotatable about said pintle, a rotary member o surrounding said assemblies and rotatable therewith and being provided with a plurality of pairs of opposed faces normal to the respective piston and cylinder assembly axes, the outer of which faces constitute reu action faces, cross heads connected with said piston and cylinder assemblies and each being guided for reciprocation between the faces of one of said pairs of opposed faces, and substantially plane faced bearing blocks yin- 4 terposed between said reaction faces and the associated cross heads and being carried by one and slidably engaging the other in bearing relation thereto.

In witness whereof, I hereunto subscribe u my name this 9 day of January, 1931.

ELEK BENEDEK.

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