US2016812A - Pump - Google Patents

Description

2 Sheets-Sheet l N\ 4 I Q mh 3/? 0m II 1 Tm E. BENEDEK Oct. 8, 1935.

Filed March 21, 1932 RA/QQ Ot. 8, 1935. E. BENEDEK' 2,016,812

' Filed March 21, 1952 2 Sheets-Sheet 2 Patented Oct. 1935 I UNITED STATES PATEN 'liO'FFlCE rum Elck Benedek, Mount Gilead. Ohio Application March 21, 1932, Serial No. 00,19.

15 Claims. (oi. 103- 401 This invention relates to variable delivery pumps and motorsjof the internally driven rotary piston type. for use primarily in high pressure 'fluid transmission systems.

5 Pumps and motorsof. the type herein above renecting rods bearing on'the periphery of of the connecting rods between the eccentric ferred to include ordinarily a variable stroke mechanism comprising a stationary eccentric shaft made by an outer eccentric member and an inner eccentric member, and the outer eccentric member is provided with mechanism whereby its angular position on the inner eccentric member can be varied to thereby vary'the stroke of the pistons in the cylinders, the pistons having conouter eccentric member. u

The purpose of the present invention is to simplify the variablestroke mechanism and provide a single rotary member thereof. The elimination member and pistons will provide a novel connection between the rotary member or planetary eccentric and the associated pistonsfin which the direction of each hydraulic piston load will coincide with the axis of the reciprocation of the piston and eliminates'the wearvon the cooperative surfaces of piston and cylinder assembly, and

thereby increases the efliciency of the pump or motor.

According. to the spirit of this invention 'a single rotary planetary eccentric is used Ior'the drive of the pistons.- Universal coupling means are used between the planetary eccentric and the impeller shaft to allow transverse shift or the planetary eccentric member. The pump and motor may have the same constructlon. however the eccentricity oi the motor is ordinarily constant and this eliminates the stroke adjust- V ing mechanism from the motor.

- v The pistons areaof the crankless T-head type, provided with a tangential crosshead rigidly .connectedtothe'piston propertooperate thepisdirections.

Another novel feature of sistsoftheprovisionoiapumpcasing'havinga cyiindricaJ-openingat one end and a pair of tangential parallel shoulders at the other end to engage rigidly a slidable stroke controlling block.

The torque transmitting members between im-.

peller and adiustable have pure harmonic oscillation relative to their cooperative members during-rotation.

Further novelty of present pump or motor lies in the fact that duringthe operation of thepump,

the planetary eccentric is in perfect balance, including the cooperative pistons. m is evithe this invention con- .dent for the zero delivery position when the whole rotary system rotates aroundthe geometrical axis of the pump, at which time all the rotary parts are in perfect balance, It will be seen that during stroke periods of the pump the 5 radial system of pistons will effect the perfect dynamic balance also of the planetary eccentric by gettingthe crossheads more crowded at one side of the eccentric than at the other. i

. Another object of myinventionis to provide 10 a. planetating piston actuating means, whereby each piston will'have two pressure and two suction strokes during each revolution and thereby to 'eiIect hydrostatically balanced load conditions in the barrel and its double acting cylindrical 15 valve member .oripintle, whereby to unload the bearings of the barrel andeliminateseizure between. pintle and barrel. The invention is more specifically described in 7 connection with the. attached drawings which 20 'sliow onejorm ot the inventive idea.

In the drawings:

Figure 1 is a longitudinal horizontal sectional view of a pump constructed in accordance with; present invention. is taken on the 25 horizontal main axis-of the pump, on line. l--I in Fig. 9. s

2isatransversesectionalviewtakenon line'l-linllgurc-l.

averflcalcrosssectiontaken on 9 inligurel. pumpshowninthedrawlngsisenclosed comprisingahollowcylindrical case ll closedatitscndsbyendcovers II and respectively. The parts of thehousing constitute aliquidtightreservoirwithiootportions l3 and It for the mounting of the pump on a suitable bed plate.

'lhes'tatlonal'ydistributororpintlellisrisidly secured'inthehub portion ll'otendeover l 2 vand projects inwsrdlyinto-thecasingtoengage a rotarycylindcrbarrel lisuwor atitsends onanti-irictlolibeaflngs It and I1, withthevlew u to center the barrel withflrespect to the pintle, and eliminate wear and metallic friction therebetween and provide a continuous capillary oil film also. Planetary eccentric I8 has two fiattenedend portionsas at H! and 20 respectively which are set at 90 degree position with respect to each other. A plurality of tangential grooveways 2| are provided to receive the associated crossheads 22 of piston 23. The pistons are fitted for radial reciprocation in their associated cylinders 24, and are removable through radial pipe plugs 25. The planetary eccentric l8 has a plurality of peripheral T-slots 2| with lip portions 26 p to effect the suction stroke of the pistons whereas the pressure stroke is effected by the tangential reaction surfaces 21, the bottom surface of the T-slots 2|. End portion I9 of the planetary eccentric IB is fitted in the slotted portion 28 of the cylinder barrel |5-for sliding reciprocation as shown in Fig. 2 supported on oil film or on proper anti-friction bearings. The slotted groove-way 28 of the cylinder barrel cooperates with the slotted groove-way 29 of a rotary adjustable member 30, and they are set 90 degrees apart in regard to each other as illustrated in Fig: 1 and transverse sections of Fig. 2 and Fig. 5 respectively. Cylin-- ders 24 are in communication alternatively during their rotation with distributor ports 34, 34, 35 and 35 respectively as shown in Fig. 3. Centrifugal channels 33 lead into the cylinders 24 which are in communication with suction and or delivery passages 3|, 32, 38 and 39 respectively.

Referring to Fig. 6 it will be seen that each pump port 34, 34, 35 and 35' is in axial communication with a corresponding valve end head port as shown in the figure, S, D, S, D respectively through axial passages 3|, 38 and 39, 32 respectively.

With further reference to the figure, the diametrically opposite ports in the head l2 are in communication with each other as indicated in the figure through appropriate pipings. The flow of fluid between one set of ports of S and S respec tively is shown and the direction is indicated by the arrows 31 whereas the similar connection between the delivery ports D and D, is shown as at the arrows 36'. The main inlet and outlet reversible ports orpump mains 36 and 31 provide inlets and outlets for aforesaid S, S and D, D chambers respectively. The outside oil circuit is connected to said pump mains by heavy pipe flanges in a well known manner.

With reference to Fig. 3 it is evident that in ports 34 and 35 or 34 and 35', there is the same vide for the axial misalignment of the planetary eccentric and the pintle. Rotary member 36 furthermore has an axially extending flat portion 41 for radial reciprocation in the cooperative fioating member 48 and for the transmission of the torque of the concentric impeller shaft 50 through the axially extending fiat portion 49 of the fioating member 48 as shown in Figs. 4 and 7 respectively. Impellershaft 50 is supported on antifriction bearing 5| and packed against leakage by packing rings 52 and packing gland 53 which latter is fastened to end cover by cap screws 54.

In Fig. 1 anti-friction bearing l6 may be directly mounted on end cover I2, instead of on 5 the enlarged portion of the distributor M which is supported by end cover l2.

As previously pointed out when rotary member 30 is adjusted laterally in eccentric position in regard to the center line of the rotating cylinder 10 barrel, the pistonswill resume reciprocation in their cylinders, due to the characteristic motion of member l8.

It follows from the foregoing analysis that since the planetary eccentric I6 is fully balanced, it 55 will operate in a distinct and different manner with respect to the control member 30, than any piston actuating member heretofore known in variable delivery pumps. Since the rotor I8 is unloaded, its supporting end flats are also un- 20 loaded. This is particularly important for the control member 36, since it is supported in bearing means such as 4| and 42, which have substantially very short span, consequently an unbalanced load at the left end thereof by flat 26 as 25 shown in Fig. 5 would impose considerable transverse load therein, which would result in sudden wear, or too expensive bearing structure for the support of member 36. It is further evident that the balanced performance of the control mem- 30 her 30 will allow balanced operation for the adjacent coupling member 48 and the driveshaft 50 respectively, so that these last named members will transmit only driving torque, and will be free of any lateral or transverse bending stresses which 35 is not true in pumps of present commercial design as hereinabove referred to. The novel working method of my planetary piston actuating means l8, thus further results in any easy shift of member 46, the bearing housing of the stroke 40 control mechanism, since there is no transverse force which would act in the bearings 4| and 42 and between their housing 40, and control means The individual cylinder and piston assemblies 45 on the pressure sides will be under the hydraulic load of the fluid. Piston crossheads 22 will take up at all times the entire piston load, the crosshead and crosshead way being always perpendicular to the direction of reciprocation. This 5 advantage of the crankless piston construction is increased by the fact that virtually all the driving of the cylinder barrel is effected mechanically by the fiat portion I9 of the rotary eccentric la instead of by the piston units themselves. 55

The fluid capacity in passages 33 provides compressibility for the pistons in their outer dead centers at the end of the compression cycle, when cylinder ports 55 are blocked off for. a. certain length of time, by the positive laps of the bridges 6 56, 56', 51 and 51' respectively, as shown in Fig. 3, wherein the cylinder ports 55 are considerably smaller than the length of the bridges.

Further purpose of passages 33 connecting the outer ends of the individual cylinders 24 is in 65 the provision of positive centrifugal pressure for thesuper-charging of the cylinders during the suction stroke. This condition provides a better filling of the cylinders and a greater volume of pump delivery which means higherefiiciency of '7 the pump and more silent operation thereof. Although an even number of pistons .are shown in th drawings for the simplicty of illustration, any other number'of pistons may be used according to the requirement of theduty for which the de- 75 pure harmonic motion during its strokes. It is well known that the combination of uneven hum;-

ber of pistons will deliver smoother current than the combination or next greater number of pistons. For this well known reason, where a uniform stream of pressure fluid is required, ordinarily the minimum number oi piston and cylinder assembly comprises flve units.

In order-to increase the efliciency or the relatively sliding members in the pump, various provisions may be made to retain a certain amount 01' the slip for useful lubrication. Although such provisions are not shown in the drawings, it is understood for instance that the counter-bored end portion of the cylinder barrel which surrounds the eccentric-may be provided with an end.

abutment with the barrel end l5, so as to retain a certain amount of slip past the several pistons to keep the crossheads flooded in centension members with oil. The case l0, however, will be drained to avoid viscous friction on the rorevolution of said rotor.

tating barrel and the churning up oioil.

The operationoi the pump is as follows: Irnpeller shaft." will be driven by a suitable power such as an electric. motor, Diesel engine or alike. Asprevimsly" described theright hand support flat or the planetary eccentric i8 is engaged slidingly in the slot 28 of the adjustable relative eccentric 3|, whereas the left hand support flat I! is guided in theslot 2B of the rotary barrel l5,

' thus the two endflatsoi the planetary eccentric are supported and driven between or by two parallel-but axially offset members IS and 30 respec- .tively, and forming with them the floating member of the well known Oldham coupling. 'I'herefore, so far as all the three members l5, II and 30 dorotate about a' common axis such as the axis of the pintle I, or the rotational axis of the impeller shaft", said three members will have a strokes during each revolution, with thesubsebodily rotation and no planetating takes place between the driving 30 and driven i5 coupling members. -As soon as, however, the end members i5 and 3! willbeset to an axially ofi set position,

- which is done here by the shifting'ot the bearing housing 40 through its control rods 43 and 44 respectively in either direction, the'planetary eccentric will begin to planetate and an average point .of-its periphery will describe an oval shape path in the space, which path is known'as the curve of Pascal :or Pascal Limacon. Thereiore, it is evident, that each 22 being driven and actuated by a slot if or the planetary eccentricwill have two approaches and two retreats during each revolution, with the result of what is termed adouble acting pumpoperation, by givmg each piston'two suction and two. pressure quent result of hydrostatic balance of all hydraulic members and mechanical balance of all rotary members.

Assuming pump main flias main intake connectio "(see Fig.6) the fluid will be suckedinto.

. chambers S and S" which are in direct communi- I cation'through passage 58, or equalizing pipe con- 7b nections i9. chambers S and S thefluid" v 3 Pump ports u' and as will'discharge its fluid through axial passages 32 and 38 of the pintle and thus the fluidvwill reach exit ports D and D Y and the exit main 36 otthe pump. Ports D and D are again equalized by piping 60 and cross pas- 5 sage ii of the pintle.

.Various changes may be made in the detail design of the invention hereinabove specifically described without parting from or sacrificing the.

invention as defined in the appended claims.

What is claimed is,

v 1. In a pump or motor or the character described, the combination with a casing, of a pintle rigidly secured therein and projecting into said casing, a rotor rotatable on said pintle, compris- 15 ing a barrel portion at one end and a circular flange portion at. the other end, a radial series of cylinders carried by said circular flange por-. tion, pistons for said cylinders to form a plurality of pumping units with the cylinders, piston ac- 2o 'tuat-ing means associated with said pumping units, an internal oil circuit formed with said pintle and said rotor to distribute. the working fluid of said pumping units, saidpiston actuating means including planetating means to effect two pumping cycles in said pumping units ior'each 2. In apump or. motor of the character described, the combination with a casing, of a pintle rigidly secured therein and projecting into said casing, a rotor rotatable-on said pintle. comprising a barrelportion at one end and a circular flange portion at the other end, a radial series of cylinders carried by said circular flange portion, pistons iorsaid cylinders to form a plurality of pumping units with the cylinders, piston actuating means associated with said pumping units, an internal oil circuit formed with said pintle and said rotor to distribute the working fluid of said pumpingunits, said piston actuating means illeluding planetating means to effect two pumping cycles in said pumping units for each revolution of said rotor, and meansassociated' with said planetating means to vary-the amplitude of the planetation and thereby the stroke of the pumping units.

3. In a pump or motor oi the character described, the combination with a casing, oi a pintle rigidly secured therein and projecting into-said casing, a rotor rotatable on said pintle, compris- 5o i ng'a barrel portion at one end anda circular flangeportion at the other end, a radial series of cylinders carried by said circular flange portion,-pistons for said cylinders to form a plurality of pumping units withthe cylinders, piston actu- 35 ating means associated with said pumping units, an' internal oil circuit formed, with said pintle and said rotor to distribute the working fluid of saidpumping units, said piston actuating means" including planetating means to eflect two pump- 00 ing cycles in said pumping units for each revolutle in onerend of the casing, a cylinder barrel, vrotatably supported in the casing, acylindrical flange portion elk-tending at one end or the barrel,

'piston actuating means within said cylindrical flange portion.) radial series of piston and cylinder assemblies tor said cylindricalflange portion and surrounding said piston actuating means in Working relation therewith, driving means projecting at the opposite end of the casing, coupling means intermediate said driving and piston actuating means respectively to support one end of said piston actuating means, and be driven therewith and means associated with aforesaid coupling means to transversely vary the axis of said coupling means with respect to said driving and piston actuating means respectively to thereby vary the motion of the piston actuating means and the stroke of the pistons.

5. In a pump or motor of the character described, the combination with a casing, of a pintle, a barrel, bearing means for both ends of the barrel mounted in the casing, a cylindrical flange portion extending at one end of the barrel, piston actuating means within said cylindrical flange portion, a radial series of piston and cylinder assemblies surrounding said piston actuating means in working relation therewith, an internal oil circuit formed in said casing and barrel to provide a hydrostatically balanced load transmission between said pintle and said barrel, to unload the bearing means of the barrel, driving means projecting at the opposite end of the casing, coupling means between said barrel and said piston actuating means and intermediate said driving and piston act-uating'means respectively, to adjustably support the ends ofsaid piston actuating means, and means associated with the last mentioned coupling means to transversely shift the axis of said coupling means with respect to said driving and piston actuating means and thereby vary the stroke of the-pistons, and the delivery of the pump.

6. In a pump or motor of the character described, the combination with a casing, of a pintle in one end of the casing, a cylinder barrel, rotatably supported in the casing, a cylindrical flange portion extending at one end of the barrel, piston actuating means within said cylindrical flange portion, a radial series of piston and cylinder assemblies for said cylindrical flange portion and surrounding said piston actuating means in working relation therewith adjustably mounted driving means for one end of said piston actuating means, in transversely adjustable relation thereto, bearing means for said adjustably mounted driving means, stationarily mounted driving means projecting at the opposite end of the casing, planetating coupling means between said adjustably mounted and said stationarily mounted driving means respectively, and means associated with last mentioned driving means to vary the eccentricity of said adjustably mounted driving means and thereby the stroke of the pistons and the delivery of the pump.

7. In a pump or motor of the character described, the combination with a casing, of a planetating member, bearing means in the casing for said planetating member, supporting means in said bearing means for said planetating member, transversely adjustable means guided in the casing for changing the relative position of said supporting means, to thereby cause the planetating of said planetary member, a radial series of piston and cylinder assemblies grouped about said planetating member and operated thereby, and means to adjust the relative position of'said supporting means to vary the amount of planetating and the amount of the stroke of said assemblies.

8. In a pump or motor or the character described, the combination with a casing. of 2.

casing for changing the relative position of said 5 supporting means, to thereby cause the planetating of said planetary member, valve-means in the casing, a'stationary pintle in association with said valve means, a barrel rotatably mounted on said pintle and having a radial series of coopera- 10 tive port openings, a radial series of piston and cylinder assemblies in said barrel grouped about saidplanetating member and operated thereby, communicating channels between each cylinder barrel port and the outside end of each cylinder 15 of said assemblies, control means to adjust the relative position of said supporting means to vary the amount of planetating and the amount of the stroke of said assemblies, driving means adjacent to said planetating means and means intermediate said driving and planetating means to transmit the driving torque of said driving means to said planetating means.

9. In a pump or motor of the character described, the combination with a casing of a 25 planetating member, bearing means in the casing for said planetating member, supporting means in said bearing means for said planetating member, transversely adjustable means guided in the casing for changing the relative position 30 of said supporting means, to thereby cause-the planetating of said planetary member, a radial series of piston and cylinder assembliesgrouped about said planetating member and operated thereby, means to adjust the relative position of said supporting means to vary'the amount ,of, planetating and the amount of the stroke of said assemblies, crosshead means associated with the pistons, and means formed with said planetary member to provide positive driving connection 40 between each piston and said planetary member L in two directions.

10. In a pumpor motor of the character described, the combination of a casing, a stationary pintle, a rotor having at one end a barrel portion mounted on said pintle, and at its other end an axially extending circular flange surrounding a circular space, a radial series of cylinders in said flange and opening into said space, pistons in said cylinders, valve means in said pintle, pas- 50 sage means provided in said rotor betweenvsaid valve means and the outer ends of said cylinders for the supply and discharge fluid respectively,

'driving means for said rotor, piston actuat ing means associated with the inner ends 5 of said pistons, torque transmitting means between the barrel portion of said rotor and said piston actuating means, said torque transmitting means comprising an axially extending flat portion of said piston actuating means,v and so a receiving groove in said barrel in reciprocating bearing'relation thereto, and means associated with said piston actuating means to vary the stroke of the pistons and the delivery or the pump.

11. In a pump or'motor of the character described, the combination of a casing, a stationary pintle, a rotor having at one end a barrel portion mounted on said pintle, and at its other end an axially extending circular flange sur- 70 rounding a circular space, a radial series of cylinders in said flange and opening into said space, pistons in said cylinders, valve means in said pintle, passage means provided in said rotor between said valve means and the outer ends 7 of said .cylinders for the supply and discharge fiuid respectively, driving means for said rotor, piston actuating means associated with the inner ends of said pistons, torque transmitting means between the barrel portion of said rotor and said piston actuating means, said torque transmitting means comprising an axially extending flat portion of said piston actuating means, and a receiving groove in said barrel in reciprocating bearing relation thereto, and means associated with said piston actuating means to vary the stroke of the pistons and the delivery of the pump, said means including a rotary torque transmitting means mounted in the casing, a flat extension projecting from said piston actuating means, and a mating cooperating slot provided in said torque transmitting means, to transmit the drivingrtorque of said torque transmitting means to said piston actuating means while the one being adjusted withrespect to the other.

12. In a pump. or motor of the character de scribed, the combination of a casing, a stationary pintle, a rotor having at one end a barrel portion mounted onsaid pintle, and at its other end an axially extending circular flange surrounding a circular space, a radial series of cylinders insaid flange and opening into said space, pistons in said cylinders, valve means in said pintle,

passage means provided in said rotor between said valve means and the outer ends of said cylinders for the supply and discharge fluid respectively, piston actuating means associated with the inner ends of said pistons, control means associated with said piston actuating means, coupling means between said control means and said piston actuating means, driving means coaxially disposed withthe rotor, a secondary coupling means between said driving means and said control means to adjustably engage one end of said control means and the adjacent end of saiddriving means respectively. 1

13. In a pump or motor of the character de scribed, the combination of a casing, a stationary pintle, a rotor having at one end a barrel portion mounted on said pintle, and at its other end an axially extending circular flange surrounding a circular space, a radial series of cylinders in said flange and opening into said space, pistons in said cylinders, valve means in said pintle, passage means provided in said rotor, between said valve means and-the outer ends of said cylinders for the supply and discharge fluid respectively, piston actuating means-associated with the inner 'ends of said pistons, control means associated with said piston actuating means, coupling means between said control means and said piston actuating means, driving means coaxially disposed with said rotor, a secondary coupling means between said driving means and said control means to adjustably engage one end of said control means and the adjacent end of said driving means, said means comprising a torque transmitting planetating member, having flat extension portions at its ends in crosswise relation, and cooperative slots, provided in the respective ends of said control means and said driving means.

14. In a pump or motor of the character de scribed, the combination of a casing, a stationary pintle, a rotor having at one end a barrel por- 5 tion mounted on said pintle, and at its other end an axially extending circular flange surrounding a circular space, a radial series of cylinders in said flange and opening into said space, pistons in said cylinders, valve means in said pintle, passage means provided in said rotor between said valve means and the outer ends of said cylinders for the supply and discharge fiuid respectively, piston actuating means associated with the inner ends of said pistons, control means for said piston actuating means, supporting means for said piston actuating meansto planetate said piston actuating means, said supporting means comprising a flat portion carried by said piston. actuating means at each end thereof and a receiving straight groove in the adjacent ends of said rotor and said control means respectively, fixed driving means adjacent. to said control means and means between said driving and control means to provide free adjustment 25 for said control means with respect to said driving means during the rotation of said fixed driving means. 1

15. In a pump or'motor of the character described, the combination with a casing, of a pintie rigidly secured therein, a cylinder barrel rotatably supported in the casing and on said pintie respectively, driving means for said rotor, a cylindrical flange'section carried by one end of said cylinder barreland extending axially thereof, supporting means on each end of said barrel, bearing means for said supporting means, cylinders in said circular flange portion, pistons for said cylinders, a crosshead associated with each pist0n,'valve means provided in the pintle, fluid supply means between the pintle and the.

' cylinders, piston actuating means, associated with the crossheads, said means including a planetating member having circumferentially disposed groove ways to operatively engage the 45 piston cross heads for reciprocating the same,

control means adjacent to said piston actuating means to vary the amplitude of planetation of said piston actuating means and thereby the stroke 'of the pistons, torque transmitting means between said piston actuating means and said barrel and control means respectively, and planetating means between said control means and said driving means, to thereby maintain driving relation between said driving means and said 5 spaced radial bearings mounted in said housing,

arotor for saidradial bearings and means to secure said bearings on said rotor.

ELEKBENEDEK. c5

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