US2189773A

US2189773A - Hydraulic pump or motor

Info

Publication number: US2189773A
Application number: US35480A
Authority: US
Inventors: Elek K Benedek
Original assignee: Individual
Current assignee: Individual
Priority date: 1935-08-09
Filing date: 1935-08-09
Publication date: 1940-02-13
Anticipated expiration: 1957-02-13

Description

6 Sheets-Sheet 1 Feb. 13, 1940. E. K.`Bx:NEDEK HYDRAULIC PUMP OR MOTOR piled Aug. 9, 1955 v. mm M M m n o. .wN V E l n m m m m nu Nm. 1 K ,fi/ l KA N ful/. E 1 Nw n L Q l ,N @QN SMM `.|1 |!.|a| bha, I l h@ w3 X Mw, @A NT BIL ,il i w NS XR. i NNMIVI .Q I hm w m s. um A. mw b .MQW/f .Q Q Si@ ww NN, I N wv :www //.nw www %N h. N, m.. h. lrl, w\\. mi d. l @n ,NQ www NIL Feb. 13, 1940. E. K. BENI-:BEK 13,189,773

' HYDRAULIC PUMP OR MOTOR Filed Aug. 9, 1935 6 Sheets-Sheet 2 -Z INVENTOR.

j OZ

` ELEKK'JENEDEK;

ATToRNEY.

E. K. BENEDEK HYDRAULIC PUMP-0R MOTOR Feb. 13, 1940.

Filed Aug. 9, 1.93.5 l s sheets-sheet 3 INVENTOR. ELEKKEI ENI-:DBK

EE. v

Feb. 13, 1940. l E; K BENEDEK 2,189,773

Y HYDRAULIC PUMP 0R MOTOR'- Filed Aug. 9, 1935 6 Sheets-Sheet 4 Feb. 13., 1940. l

ra.l K. BENEDEK r2,189,773

HYDRAULIC PUMP 0R MOTOR I v Filed Aug. 9, 1955 s'snets-sheet 5 'ELEM/ 2 EENEDEK 15.11f 3mm Fel). 13, 1940. I K, BENEDEK 2,189,773

HYDRAULIC PUMP 0R MOTOR Filed Aug. 9, 1935 6 Sheets-Sheet 6 5 7 a@ as T1512 5 l V a IN VENTOR.

Y E. EKKB ENEDEK B i ATTORNEY.

Panarea Feb. 13, 1940 fum-TED STATES, PATENT oFFlcE nrnnauucislL-on Moron i nsekiesoysleuraxo 35,4'sc 7 ciaims. ici. ica-161) This invention relates to hydraulic pumps and and pintle mounting of such character that asmotors of the rotary, radial plunger type, emsembly and disassembly ofthe parts for repairs playing rotary reactances, and particularly to and inspection are greatly simpliiied and pumps and motors of this character for use in facilitated. v

' connection with hydraulic transmission systems. Another object is to provide a variable delivery 5 The principal kobject of the present invention 'motor having a. large capacity ratio relative to is to provide a simplied, compact, and eillcient, the pump but with a suiiiciently long stroke to rotary reactance which may be manufactured provide greater flexibility in adjustment for efand installed more economically than those here- .fecting a. wide range of speed, power and torque m tofore employed and which is adapted for acwith high eiiciency throughout the rang. 3 curacy in' manufacture by quantity production Other objects and advantages will become apmethods employing simple and well understood parent from the following specification wherein machining operations and standard tools and reference is made. to the drawings inwhich equipment. Fig. 1 is a. horizontal sectional plan view of a Another object is to provide a rotary reactance hydraulic transmission mechanism embodying l5 having a very great working-resistance radially the principles of the present invention; for withstanding radial load as a result of which Figs. 2- and 3 are vertical cross sectional views the axial dimension of the reactance can be retaken on planes indicated by the lines 2-2 and duced. 3-3 respectively of Fig. 1;

20 Another object is to provide a rotary reactance which is drivingly connected to the barrel of the pump or motor by the plunger actuating means in such a manner that separate or accessory mechanical coupling devicesvare eliminated.

w' A. more specific object is to provide a plurality of axially floating rotary reactance rings and axially oating plunger actuating means which cooperate with the opposite ends of the plunger Ain a manner permitting elimination of accessory clamping means between the vrings and permitting free but limited axial iloatins movement of the rings with respect to each other and to the plunger actuating means whereby therings and actuating means are self-adjusting axially with respect. to each other and to the4 cylinder barrel and plungers.

:A correlative object ls to provide a novel antifriction mounting for the reactance. ,i Y Another object is to provide a ilexible starting tary reactance used in connection with the present invention showing the rotary reactance as a sub-assembly; and is taken on a. plane indicated bythe line I-l inFig. 5;

Flg. 5 is a sectional view of the reactance rotor subassembly of Hg. 4 and is taken on a plane indicated by the line 5-5 thereof;

Fig. 6 is agfragmentary sectional view similar to Fig. 4 illustrating a modiii'ed form oi rotary reactance and is taken on a plane indicated by l@ the line 6--8 of Fig. 7;-, y Fig. 7 is a sectional view of the rotary reactance illustrated in Fig. 6 and is taken on the plane indicated by the line 'l-I of Fig. 6;

Fig. 8 is a vertical sectional view through a 35 stationary rotary reactance housing an associated rotary reactance illustrating another modification of the reactance; f

Fig. 9 is a fragmentary sectional view taken Fig. 4 is an enlarged sectionalview of the ro- :il

means between the plunger actuating means and the rotary reactance which means are rendered active to provide the driving connection by centrifug'al force so as to eifect al more gradual apon the plane indicated by the line 9-9 in Fig. 8; Fig. 10 is a vertical sectional view throughv a stationary reactance housing and associated rotary reactanceillustrating another modication j preach to synchronous rotation of the barrel and of the reactancy Y i fmmggughgggbgedgggg and, im@ fesse m.. u is s fragmentary ...am View aan Anotherobjt is to incisa uw safety factor on the plane indicated by the line II-II on Fig. of um or motors with reference to the load *10;

n; assgciation ot the various-working parts so F18 12 1S fragmentary longitudinal @mm1 .10:55: n lrtisfnotattoozauseeilsplacemagnueogc; grt r otherppmand con. lar to that on which Fig. 1 is taken .and showing e- -,Jnkseguent break-down or failure of 1 the pump or mdied multiple plunmlv Pump 0I 1301102 einmoikgti-immuniYY ploying the rotary reactancemeans ofthe pres,-

Stlll another object is to provide'a rotary reent invention. l actance. plunger actuating connection. barrel im, 13 is a fragmentary sectional view illusf `lsectional view taken on a horizontal plane simi- .0

trating a novel anti-friction mounting for the rotary reactance.

For the purposes of illustration, the present invention is shown embodied in both a pump 5 and a motor, the pump and motor being co operated in a hydraulic transmission and both being of the rotary, radial plunger, reversible, variable displacement type. Both the pump and the motor are mounted in a casing, designated l0 generally as I, having a central valve portion 2 which terminates at its ends in

radial Aflanges

3 and 4 respectively. The flanges, in turn, are provided at their outer margins with annular, axially extending walls 3a and 4a respectively, forming compartments for the pump and motor. The ends of the casing are closed by -suitable

rigid end covers

5 and 6 respectively which are bolted to the ends of the annular walls 3a and 4a so that a rigid unitary casing structure, in which $0 al1 necessary axial bores and shoulders can be machined readily and coaxially for assembly in accurate alignment with each other, is provided. In the left hand compartment ofl the casing is mounted a pump, and in the right hand 26 compartment is mounted a motor.

Referring first to the pump structure, the pump comprises a rotatable barrel I 0 which has a coaxial impeller or drive sha-ft Illa, preferably forged integral with the barrel for purposes here- 30 inafter set forth. The barrel is rotatably mounted in the casing portion 3a on coaxial sets of combination radial load and axial thrust antifriction bearings II and I2 respectively. The sets of bearings II and I2, in turn, operate on inner races which are xedly secured on. hub or end portions of the barrel I0, as illustrated, and outer races which are xedly secured against approprlate shoulders in the ange 3 and end cover 5U "5 I2 may be pre-loaded to the degree necessary to assure accurate positioning of the barrel and to compensate for wear;v

On the barrel I0, between the hub portions, is a'radial flange I4 which is preferably lforged inw tegral with the barrel and has smooth, polished, radially extending end walls. In the zone of the flange I 4, the barrel has a plurality of circumferentially spaced radial cylinders I5, each oi' which cylinders is provided with a cylinder port u It in communication with an axial valve bore of the barrel I0 for e'ecting valving cooperation with a valve pintle, later to be described. The flange I4 is provided with radial guide ways I'I, each guldeway being aligned and coaxial with an .o associated cylinder I5. The radially extending walls of the guideways I1, in advance of and to the rear of the associated cylinder, are cylindrical.

Mounted within each cylinder is a radial 66 plunger I8, having at its outer end an enlarged crosshead I9, the crosshead having cylindrical front and rear walls snugly fitting the cylindrical walls of the guideways I'I for reciprocation therealong, the crosshead being prevented from move- 70 ment endwise of the ange by the mating cylindrical surfaces.

'Ihe lateral faces of the heads I9 are smooth and polished so as to define, with the radial respective end walls of the ange, substantially con- Il tinuous radial surfaces. Each of the heads I9 has a pin receiving bore which extends parallel to the axis of rotation of the barrel and in which is received a journal or crosspin 20. The pin 2l extends beyond the lateral limits of the crosshead in each direction, the extending portions 20a be- 5 ing of less diameter than the central portion and being in cooperation with the rotary reactance 22 for reciprocating the associated piston. Suitable rounded shoulders 20b are provided between the central and end portions of the pins for enl0 gagement with the rotary reactance for purposes hereinafter set forth. The pins 25 are rotatably supported in their associated crosshead bores on suitable capillary cageless needle rollers 2|, the ends'of the bores being closed by suitable l retaining washers for maintaining the rollers in position axially of the bore. In this manner the pins may float axially relative to the associated crosshead and resistance to rotation of the pins in the crossheads is less than between the pin 20 ends and rotary reactance, thus assuring rolling load transmission. v

For actuating the plunger through the medium of the pin ends 20a, coaxial rotary reactance rings 22 are provided. It is necessary for economy 25 in manufacture and to meet commercial competition, that the rotary reactance be simple, compact, and durable, that they be of such form that they may be manufactured accurately and economically, that they be so associated with the '30 plungers that ease and accuracy in assembly and disassembly are assured. In addition, the reactance must be capable of withstanding severe radial loads, must cooperate efciently and acn l. curately with the plungers at all times, and must I6 be of reasonable dimension axially.

For meeting these requirements, each of the rings 22 is preferably of rectangular cross section having parallel radially extending end faces which are hardened and accurately polished as u, also is the outer circumferential wall. Two such rings are provided, one at each end of the barrel flange, and the rings are disposed with their adjacent end faces in substantially face to face relationship with the end faces of the flange Il, m operating clearance only being provided between the flange and rings for permitting the entrance of slip fluid therebetween. The rings are rotatably mounted in a suitable housing later to be described, for rotation about an axis parallel to, u but offset from, the axis of rotation of the barrel I0. Each ring 22 is provided with a series of circumferentially spaced grooves 22a which extend endwise of the rings entirely therethrough, forming slots and may be arcuate, as illustrated, or;-M chordal, depending upon the particular unit in which they are to be used. The grooves of each ring are aligned axially of the rings with respect to the grooves of the other and receive and snugly accommodate the reduced end portions of the,"0

pins 2II.

The grooves 22a are preferably mrmed by boring spaced holes in each ring parallel to the ring axis, and then machining out the intervening material so that the ends of the grooves are arcuate and correspond accurately in radius to the radius of the reduced end portions 2.a of pins. Thus smooth operation in starting and stopping is provided by proper seatingol' the pin ends against the cylindrical ends of the grooves. 10

The crosspin end portions 25a are of sumcient length to extend entirely through the grooves and slightly therebeyond past the outer end faces of the rings. As better illustrated in Fig. 5, these protruding end portions are recessed circumferen- Il terval and the .centrifugal tially adjacent the plane of the outer end faces of the rings 22. Snap washers 22 are disposed in .the recesses and accommodated therein with slight axial clearance and engage the end faces of the rings to constrain them from axial separation.

Since theplns are mounted on capillary bearings 2| and may float axially in the bores of the crossheads, and since clearance is provided between the washers 23 and the rings 22, limited floating movement between the end portions of the'pins and the rings is provided and both the rings and pins may adjust themselves axially to proper operating position with respect toeach other and to the crossheads and barrel flange. Due to the shoulders 20h, accurate spacing of the rings axially is assured. This selfadjustment requires also that the rings 22 be mounted for axial floating movement in ltheir supporting means. v

For supporting the rings 22 in this manner, an

adjustable reactance housing 24 coaxial with the rings, is mounted in the casing portion 3a. The housing 24 is supported in surrounding relation to both rings 22 and ev tends axially therebeyond. The portions of the housing 24 aligned radially with the rings are recesses circumferentially, as indicated at 24a. Sets of elongated free needle rollers are accommodated in the recesses 24a, v

the recesses preferably being in depth substantially thesame or slightly less than the diameter of the rollers 25 so that the end portions of the housing constrain the rollers from axial separation and form lubricant retaining troughs. In the form illustrated, two such sets of rollers are provided. one for each reactance rlngjrespectively, gaging both of tle rings 22-` may be utilized providing the length-diameter ratio remains less than een. 1

The rollers 25 are rst packed betweenV the housing 24 and rings 22, and two or three rollers of each set are then removed so that the total clearance circumferentially of the housing 24 is onlysumcient to provide capillary clearance between the individual ers and arrangement thereof described in my United States Letters No. 2,074,202, issued March 16, 1937. Y.

In this mounting, the circumferential surface of eachof the rings 22 is `finished with great precision and hardened to withstand wear as above mentioned. The bottoms of the recesses in the housing 24 are likewise precisely finished and' hardened so that accurate coaxial relationship between the housing recesses 24a and rings 22 is provided.4 this mounting of the ringsin that slip fluid may pass between the rings 22l and crossheads and between all connectedparts and into the recesses 24a where it is maintained as a pressure being more fully oilbearing by centrifugal force during the operation of the pump. However, upon stopping the'- pump, this centrifugal lubrication ceases. The rollers, however,.'tho ugh theymay not be true capillary rollers, are constrained to circumferentially spacing of only a capillary distance apart Consequently, although the entire space between the rollers and the race surfaces will not be filled with the pump has stopped for an inpressure lubrication lubricant after has ceased, nevertheless the space .between the though a' single set of elongated rollers enrollers ofeach' set, the roll- Patent Another advantage resides in will maintain- 4continuously rollers and especially be- ,tween the adjacent surface portions of ladjacent rollers. to insure proper lubrication until the centrifugal film is' again replaced. By this arrangement, the rings 22 may float axially individually relative to the housing 23 and emcient lubrication is assured at all times.

. yIn this structure, the rings must be very accurate and appreciable elastic deformation must be avoided. Consequently, the rings are sumciently rigid radially` to withstand heavy hydraulic loads and also stresses occasioned' by heat treating and hardening all without deformation, as obviously, any such deformation would immediately be reflected in the outer circumferential wall 4which forms the raceway of the rollers 25.

The rings 22 are', therefore, made radially deep and the vgrooves 22a are formed near the radial mid-portion or median, wherein the removal of ,material does not appreciably reduce the strength of the rings.

The pump, as mentioned, is of the reversible variable delivery type and consequently the housing 24 must be mounted for adjustment to diiferent positions wherein'it is coaxial with or has its axis disposed parallel to and offset from the axis of rotation ofy the barrel. For mounting the housing for adjustment, the casing portion 3a is provided with diametrically opposite parallel slide bearing surfaces 26, and complementary v slide bearing surfaces 21 are formed on the housing 24, these surfaces cooperating to support the housing accurately during adjustment.

Control rods 28 are secured on the\`housing and extend parallel to the slide bearing surfaces 26 and 21 through suitable hores in the casing, for adjustment of the housing and associated rings 22 from the outside of the casing.

In the right h and compartment of the casing, Fig. .1, is lmounted the cylinder barrel 3B of the motor, the-barrel bearing being provided with a drive shaft 30a also forged integral with the barrel. 3U.

` As described in mycopending application Serial No. 31,651, filed July 16, 1935, there is a definite relation between the eiiiciency and the stroke cylinder-diameter ratio of a pump or motor. Likewise, there is an increase in efliciency cylinder-diameter vratio is virtue of a large cylinder motor operating at ver'y short stroke, the efllciency decreases rapidly. It is desirable, especially in a constant horselassuming it is to be used for automobiles, a motor employing a set of large cylinder and plungerA assemblies might be used. This would havev an objection at a short stroke, because the stroke cylinder-diameter ratio would thenbe greatly re-. duced'- and the efllciency correspondingly de` creased.

In the present structure, therefore, a motor employing a multi-set of cylinders, for example, twin cylinders, is utilized, thus providing the large capacity relative same time affording greaterA eiiiciency in operation when the motor operates atshorter stroke,v as obviously the stroke cylinder-diameter ratio does not decrease so rapidly with the twin cylinto the pump but at the lwith an increase in size. When the strokey unduly decreased by ders as it would were a single equivalent large cylinder used.

In the illustrative motor structure, a twin plunger motor is utilized to meetthe particular speciiic demand of speed and size. The barrel 3l conforms, in general, to the barrel of the pump and is mounted in the casing in anti-friction bearings 3i and 32 respectively corresponding to bearings il and i2. Intermediate its ends, the barrel has an integrally forged radial iiange 34, and, in the zone of the ilange, a series of circumferentially spaced, radial, twin cylinders 35. The cylinders are in communication with the valve boreof the barrel, later to be described, through suitable individual cylinder Ports 33.

'I'he twin cylinders 35 are arranged in pairs, the axes of the cylinders of 4each pair lying in the same radial plane through the axis of rotation of the barrel. In the flange 34 are rad"a1 guideways 31 corresponding in form and function to the guideways I l of the pump.

Mounted in the cylinders 35 are plungers 38 having enlarged crossheads 38, respectively. which are reciprocable in and guided by the guldeways 31. The plungers are correspondingly arranged in pairs, the crossheads of each pair of twin plungers preferably being in juxtaposition at their adjacent faces and having their Aouter faces terminating substantially in the respective planes of the end faces of the flange 34. The crossheads of each pair are provided with aligned pin receiving bores extending parallel to the axis of the barrel, for receiving a single thrust or journal pin 4 0, common to both heads and having reduced end portions 40a cor'- responding to the end portions 20a of the pump.

. crosspin. Each crosspin 40 is rotatably mounted in the aligned bores of the crossheads on sets of capillary cageless needle rollers 4l, the sets of '4 rollers being spaced apart by suitable spacing gwashers, as illustrated. Retaining washers are also provided at the outer ends of the sets of needle rollers for retaining them within th bores of the associated plunger heads.

'Ihe plunger heads are so arranged and are of such width as to terminate at their outer limits, each substantially at or very close to the corresponding end face of the ilange 34, and both the faces of theplunger heads and the end faces of the ange are hardened and accurately polished so as to present smooth radial faces to resist wear and to oier the slightest Irictional resistance to any parts contacting therewith.

For actuating the twin plungers through the medium of the pins 44, a rotary reactance is provided, this rotary reactance comprising a pair of rings 42 corresponding in form and function to the rings 22 above described. The rings 42 are provided with circumferential grooves 42a corresponding to the grooves 22a of the rings 22, and in which are correspondingly received the reduced end portions 44a of the crosspins 4l. The ends 44a of the crosspins extend outwardly beyond the-ends of the rings 42 and are recessed to receive soap washers 43, the recesses being slightly greater in width axially of the pin than the'gthickness of the washers so as to provide free '-.oating limited movement between the` crosspins and the rings 42.

For rotatably supporting the rings for adjustment to different degrees of eccentricity relative to the barrel, a reactance housing 44 is provided and mounted in the casing 4a in a manner corresponding to the reactance housing 24. 'Ihe housing 44 is also recessed internally with circumferential recesses 44a in which are received free cageless rollers 45 spaced a capillary distance from each other in the same manner as the rollers 25, so that the rings 42 may iloat axially therein. For shifting the h'ousing 44 to diilerent adjusted positions, adjusting rods 48 are provided, these rods extending diametrically opposite from each other through suitable bores 42a in the casing portion 4a, the bores preferably being slightly greater in diameter than the rods so as to permit the rods to become self-aligning with respect to the housing 44.

Both the

pins

20 and 40 are provided with slightly rounded Wall portions at the juncture oi their central and reduced end portions, as described in connection with the pins 2li, and the groove edges of the associated rings 22 and 42 are correspondingly rounded, as best indicated in Fig. 5, thus providing cooperating shoulders on the pins and rings so that the rings are held in properaxial spaced relation with respect to each other by their associated pins and washers and, in turn, the rings cooperate with the end faces of the associated flanges for constraining the pins to proper axial position. Due to the particular manner of mounting the pins in the plunger heads anti-frictionally, the frictional resistance to rotation of the pins in the plunger heads is less than the rolling friction between the end portions of the pins and the associated groove walls, as set forth and claimed in my copending application, Serial No. 716,451, filed March 20, 1934, so that accidental sliding of the pins is eliminated.

Since, as stated above, the rods 48 may move slightly in the associated bores of the casing, and, since the outer peripheral walls of the rings 42 are mounted on rollers 45 for fr ee axial floating movement, it is apparent that when the plungers are mounted within the barrel cylinders and connected to the rings by the pins 4l in the manner described, the rings 42 will properly align themselves therewith and with the rollers 45 of the housing 44, and at the same time, the housing 44 may accommodate itself to different axial positions of the rotary reactance mechanism. The radial walls of the

ange portions

3 and 4 of the casing and of the end covers 5 and 6 are likewise finished accurately and smoothly and are positioned with slight axial clearance with respect to the corresponding ends of the pins 2l and 40, the housings 24 and 44, and the

rings

22 and 42. Thus, in event any part of the reactance or of the crosspin assemblies becomes loosened or is broken, the parts will be constrained from falling out of place and damaging other working parts or wrecking the structure.

As a result oi' this arrangement, the extreme simplicity of the parts, and the very reduced number of parts, afvery simpliiled, compact. eiilcient and safe structure is provided.

Before referring to thevalving cooperation and iluid pressure system, certain advantages of the present structure should be speciiically pointed out. In 'the first place the rings 22 .and 42 are of the simplest possible design yet are of the preferred design for strength and durability permitting compactness both radially and axially. Due to their extreme simplicity they may be readily machined, hardened and polished and provided with suitable grooves in accordance with such standard practices that extreme accuracy may be provided economically. 'Ihe crosspins likewise are simple and easily manufac- 'these advantages the axial thev connection between the crosspins and the rings by virtue of the washers 43 is inexpensive and very positive. In addition to floating relation rendering the parts self-adjusting adds materially to the life of the structure.

When thus assembled and connected by the crosspins, the rings and crosspins reinforce each other axially and provide a reinforced rotary reactance structure." Again, assembly and disastuied. Next,

- sembly is rendered far more easy than heretofore and is reduced substantially toa. minimum. For example, if it is desired to disassemble the pump, it is only necessary thatthe end cover 5 be removed, carrying with it the outer races of the bearings Il. Ready access is then afforded to the snap washers 23 adjacent the end cover 5. These may be readily remved and the rings 22 thereupon removed from the casing. If inspectionv of the pistons is required, the entire barrel Il) with thepistons and rings 22 may be removed in assembled condition and then the parts readily disassembled and inspected. Again, since the parts are self-adiusting and axially -iioating the dangers of undue tightening of one part relative to' another etc. upon re-assembly are eliminated.

.It is only necessary to insert the barrel and reactances as a sub-assembly and by proper shimming between the cover 5 and end of the'- casing -portion 3a secure the barrel properly in place whereupon the remaining parts will assume a proper operating position free of any binding stresses.

Again, as above explained, the flange and impeller shaft of the barrel |0 are preferably forged integral therewith. Consequently in providing the bearing hubs of the barrel. the barrel valve bore, later to be described, and in polishing the various surfaces, absolute concentricity thereof can be effected, the barrel shaft being utilized as the rotating center during these operations. This again assures absolute concentricity between the barrel shaft and the other finished surfaces so that vibrations occasioned by eccentricity of the shaft or slight angular misalignment thereof are entirely eliminated. Consequently, both efficient production and extreme accuracy are assured.

Referring next to the pressure fluid system and valving relation, the same will be described for purposesof illustration, as that of a transmission embodying the .present pump and motor.

In order to effect a proper valving cooperation between the pump and motor, a common valve pintle 50 is provided, the pintle having an enlarged rigid Acentral shank portion 5l flxedly secured in the valve portion 2 of the casing and provided with a main pressure port 52 and dia- I. metrically opposite suction port 53. Since the present structure is to operate as a transmission, the outlet of the main pressure port 52 may be blocked with the pressure ducts of the pintle in direct communication and the suction port 53 communicated with a suitable sump.

The pintle 50 extends in each direction from the casing portion 2 in coaxial relationship with the barrels I0 and 30 respectively. Each barrel is provided with a .dead end axial bore in which the corresponding end of the pintle is accurately iitted. The protruding end of the pintle associated with the pump is provided with a tapered valve portion 50a having a pressureport 54, and suction or low pressure port 55, with which the cylinder ports I6 successively communicate as the barrelv I0 rotates.

pump.

barrel. The sets of rollers The opposite end of the pintle has a valve portion 80a which fits into a correspondingly tapered bore inthe barrel'30 and is provided with a pair of pressure ports 60 and suction ports 8l, one pressure port andl one suction port being provided for each set of cylinders 35.

Pressure ducts 62 are formed in the pintle and connect the main pressure port 52 with the pressure ports 60 of the motor and with the pressure port 5l of the pump. Low pressure or suction ducts 63 in the pintle communicate the main low pressure port 53 with the low pressure ports 5| of the motor and with the low pressure port 55 of the the port 53 being connected to a suitable cooling sump, if desired. Thus a complete prossure iiuid circuit is provided. The valve portions of the pintle iitthe respective barrel bores with annular bearing surfaces are provided at each end of each valve portion of the pintle, and accommodate sets of capillary cageless needle rollers, respectively, such for example as the sets of rollers 64 and 65 of the motor, the details of which are. described in my copending applications, Serial N0. 641,186, led November 4, 1932, and Serial No.

ally aligned ycylindrical bearing race portions of the barrel bore wall. Instead of true capillary needle rollers, however, larger cageless elongated rollers may be used, but the latter should be spaced a capillary distance .from each other circumferentially of the races, as set forth in mycopending application, Serial No. 23,880, led May '28, 1935. In all instances, the main bearings, vsupporting the barrels, are preferably in radial alignment with the cageless rollers maintaining positive coaxial relation with-the 66 and 65 are sutil-y ciently strong to stress the pintle into truecoaxial relation with the barrel in those instances in which inaccuracies in manufacture or assembly would otherwise cause misalignment.

It is. apparent from the foregoing description the pintle in 'that' a highly eflicient and simple pump or motor is provided in whichthenumber of working partsv has been reduced to'a minimum and all parts areso retained that the breakdown of any one part will not necessarily damage the other parts of the pump or motor.

Slip uid from the cylinders of each structure is forced by centrifugal pressure between the operating faces of the plunger heads, barrel flange, and

reactance rings, thus affording lubrication at all times. This Auid finally passes into the recesses of the associated reactance housing which retains it on the rollers therein, forming -a circumferentially closed chamber for such iiuid. Thus slip fluidv is retained by capillary attraction and centrifugal force and provides a combination high pressure oil and anti-friction'bearlng.

.Referring next toFigs. 6 and 1, a.V novel reactance ring corresponding in function to the rings 22 is illustrated. This reactance ring, designated 23,880,1i1ed May 28, 1935, and which engage radl-` generally as 15, is one that may bemanufactured and assembled readily and in which problems-fof machining surface, grinding and they like are reduced to simple operations. The reactance ring l5 comprises a pair of coaxial rings 1G and 11 which are of the same dimensions axially, the ring 11 being of less outside diameter than the inside diameter of the ring 16. In order to space the rings in coaxial relation and to form operating grooves corresponding to the grooves 22a of the ring 22, a number of spacing vblocks 18 are provided, these blocks being circumferential segments of a single ring conforming to the clearance space between the

rings

18 and 11. The blocks 18 are inserted between the rings and evenly distributed in the circumferentially spaced relation desired, depending upon the number of grooves required and maximum eccentricity of the barrel and reactance, and are secured in place, thus spacing the

rings

18 and 11 radially and providing grooves 19 for the ends of the crosspins, as indicated at 80. The blocks 18 are held in place by suitable bolts 8| extending from the inner ring 11 outwardly and cooperating with suitable screw threads in the ring 18.

In order to mount the ring 15 directly on cageless roller or anti-friction structures in the reactance housing, the outer circumferential surfaces of the ring 16 are smooth finished and hardened and the bores in which the bolts 8| are received in the ring 16 terminate radially inwardly from the operating bearing surface of the ring. The

reason for inserting the bolts in this manner is that they will be kept in operating position by centrifugal force and looseness and danger of becoming unscrewed will be minimized.

Another modied form of reactance is illustrated in Figs. 8 and 9, wherein rings 83 and 84 corresponding to the

rings

18 and 11 are provided. In tnis structure, however, the rings are free to rotate relative to each other. The inner wall of the ring 83 is provided'with annular recesses 85 at each end and the ring 84 is provided with annular recesses 85 at each end and the ring 84 is correspondingly provided on its outer faces at the ends with recesses 86. A ring adapted to iit snugly between the rings 83 and 8l with end portions tting the recesses is provided and accurately inished. This ring is then cut into the required number of segments 81, which segments are disposed between the rings 83 and 8l and space them a proper distance apart, at the sometime forming the grooves 88 for reception of the crosspins of the plungers. The rings 83 `and 84 may be disposed in eccentric position with respect to each other and the segments 81, inserted therebetween, whereupon the segments are then generally distributed around the circumference to the desired positions so as to space the rings. This structure has an additional advantage in that upon starting or change of speed of the pump or motor the pins may engage the ends of th'e blocks 81 and move the blocks slightly circumferentially while maintaining the blocks in the circumferentially adjusted relation with respect to each other. Thus upon starting the pump or motor, the impacts which would otherwise result between the pins and blocks 81 are reduced, due to the fact that the blocks are not xed to the rings circumferentially but are positioned only by sliding frictional resistance. On continued operation, as the pressure and speed increase, the centrifugal and radial pressure between the pins and reactance exerts suicient rolling frictional driving engagement for rotating the reactances by the piston pins without `the engagement of the crosspins and blocks. As the centrifugal pressure and speed increase, the friction between the blocks 81 and the

rings

88 and 84 correspondingly increases untilthe blocks are held firmly in position circumferentially, thus providing centrifugal clutches. Consequently. hammering, due to engagement of the crosspins and the blocks 81, is substantially eliminated, and the reactance and barrel are brought to synchronous rotation more gradually. The blocks 81 do not interfere in any manner with the operation after the pump or motor has been brought to its normal speed. Thus a more simple and precise and floating cooperation between the reactance mechanism and the plungers is provided.

In Fig. l0, a one piece ring is used for each reactance ring as in Fig. 4, these rings being designated 90. Each ring 88 is provided with an annular groove 9| extending only part way through the ring axially and opening through the inner end face of the ring. Mounted within the grooves 9| are blocks 92 corresponding in function to the blocks 81 above described. Since the grooves 8|,

however, are closed at their outer faces, theblocks 82 do not need to be otherwise constrained from outward axial displacement, in which instance, plain annular segments may be disposed in the groove 8| spaced tothe position required and thereafter retained in the grooves by the iiange of the associated barrel. In this modification, however, the rings are constrained 'from axial displacement by combination radial load and axial thrust bearings 93. 'Ihe segmental blocks 18, 81, and 82 may be made of resilient or cushioning material. if desired, for reducing impact noises.

In some instances it is desirable to use pumps and motors employing a single barrel provided with a larger number of sets ofl circumferentially spaced cylinders and pistons. The present reactance assembly has many advantages when used in such connection. Referring to Fig. 12, there is illustrated a fragment of a barrel |88 having a plurality of circumferentially spaced cylinders |0l, each cylinder having a cylinder bore Il! opening into a valve bore |83 of the barrelfor cooperation with suitable ports in the valve pintle. Mounted in each cylinder is a plunger |84 having an enlarged head |85 corresponding to the heads I9 of the plunger i8. Each head, in turn, is` provided with a bore for receiving the thrust or journal pin |81, common to all aligned I plungers, the bore of each piston head being sufiiciently large to accommodate capillary rollers |08 for rotatably supporting the pin therein.

It is not uncommon in lsuch structures that the radial hydraulic loads imposed are so great that a plurality of plungers cannot be operated eiliciently by a single p in supported only at its ends without an excessively large diameter pin. Howl ever, this problem can be solved by supporting the pin at a plurality of portions, for example, both at its ends and intermediate the ends between the plungers. lAccordingly, the sets of cylinders may be spaced apart axially of the barrel so that a reactance ring of the present invention may be provided between the sets of pistonsas well as at the ends thereof.

Fig. 12 shows a. reactance ring arrangement `such as shown also on Figs. 8 and 9, including circumferentially `aaidjustablefbloclrsA 81 between:

Instead.

heads Ill 'to accommodate a rotary reactance ring which may be made in one piece or may comprise separate ring sections 03 and 08 substantially in accordance with the showing of Figs. 8 and 9, the ring or rings lying in snug engagement between the adjacent faces ofxthe crossheads, operating clearance only being provided therebetween. In addition, rings such as 83 and 0B are provided at the outer end portions of the pin |01 so thatthe pin is supported throughout its entire length either by the plunger crossheads or the reactance rings. Consequently, the pin can fail only by shearing and dangers of failure or binding, due to bending stresses, are eliminated. Thus the radial load is uniformly distributed axially of the barrel and reactance.

The pin is fioatingly mounted in the rollers |06 and is secured in place by suitable snap washers .H0 received in recesses in the pin ends in a maniler corresponding to the washers 23 of the pin 30. The intermediate rings 03 4 and 86 are mounted for axial oating movement on free cageless rollers operating in internal circumferential recesses in a common adjustable stationary reactance housing I I2, so that in the mul-v ti-piston structure, all of the reactance rings and crosshead connections may be self-adjusting axially with-respect to each other and to the barrel.

Referring next to fFig. 13, a bearing' structure for a reactance ring and having certain distinct advantagesl is illustrated. ,It is apparent that in the present types of pumps and motors, when operating at high speed, the roller elements must necessarily rotate at extremely high speeds, and, consequently, cages and retainers cannot be used with safety. To meet this diillculty, capillary cageless rollers or rollers of small diameter, such 'as set forth in my above identified applicaf i' tions, were used, these operating emcientlybecause of the elastic cage providedby the capillary oil iilms between and 'positively spacing. the rollers. The diameter-length ratio of capillary rollers is from 1 to 5 to'l to 10. In the present large structure, this ratio requirement would necessitate theuse of too great a number of needle rollers, would complicate the assembly, and be subject to imdesirable pumping effects of the needles.v The structure of Fig. 13 may be utilized vto advantagewhen. the above diameter-length ratio cannot be fulfilled on account of the limited In this structurels illustrated a barrel flange ||0 and a pair of reactance rings H9, supported in a reactance housing |20. The housing |20 is provided with internal circumferential recesses Illa. Rollers |22 are accommodated in the recesses for rotatably supporting the rings ||0 therein.

The rollers |22 have a greater diameter-length ratio than capillary needle rollers, the ratio of the diameter to the length of the present rollers being about 1:2V and 1:3. The ends ofthe rollersv :are square ground, the sharp edges only being bevelled oiI.` Correspondingly the end walls |201 of the recesses 12in. areflat and radial, the recesses being substantially equal in radial depth to'` vthe of the rollers |22. The'end walls uw een;v v

.of the rollers to positively and accurately guide cooperate with the flat ends the rollers, constraining them to substantially fixed axial position and alignment and preventing them from skewing in the recesses or races. Due to the full depth guidance at both ends of the rollers, full lateral guiding is provided, instead of the guidance afforded by the radial abutment of less than full depth, asin the case of the needle rollers of Fig. 8.

Capillary clearance walls |2011 and ends of the rollers, this clearance being sufficiently limited to. create capillary oil Yiilnis between 'the walls and ends of the rollers. For example, such clearance may b e from 0.001

vided at the ends and also between the rollers. completecapillary cages are formed for constraining the individual rollers in spaced relation to each other circumferentially of the race. Toeffect capillary spacing of the rollers from u each other, a total circumferential clearance less than the diameter or half the diameter of a sinis provided between the to 0.005 of an inch. With capillary clearance progle roller is permitted. The bearing assembly is so designed as'respect diameter of rollers and rpltchdiameter that this total circumferential clearance isfprovided.` Consequently, it is absolutely impossible for a workman to'pack the rollers circumferentially of the race and thereby prevent the'desired individual: clearances and'rotation of the individual rollersby introducing a roller to fill the total clearance space and thereby eliminate the capillary interspaces.

The total circumferential clearance depends upon the diameter of the rollers, asthe total clearance of half to almost a wholey diameter of a large roller is equivalent to several needles. Capillary space is limited .by other factors and does not vary in proportion to the diameter oi' the large rollers. Consequently, for the largest rollers, total clearance of about vone half vroller diameter may be satisfactory whereas, for a smaller roller, larger than a needle, slightly less than full diameter may be provided.

In this manner the rollers are retained in an l rotary reactance eccentric to the barrel, crosspins operatively connecting the rotary reactance and plungers for reciprocating the plungers, said re'- actance .comprising an outer ring, a coaxial inner ring in radial alignment therewith and spaced radially therefrom, a plurality of segmental blocks tting between the rings and being spaced c ircurnferentially thereof from each other to provide operating grooves, said grooves accommodating the crosspins, and said blocks being slid'able circumferentially of the rings for reducing impact forces occasoned between the crosspins and blocks by changes in the relative speed of rotation of the barrel and rings. I

2. In a rotary radial plunger pump or motor, a rotatable barrel having a set of' circumferentially spaced radial cylinders, valve means for the cylinders, plungers in the cylinders respectively, a rotary reactance eccentricv to the barrel, crosspins operativelyconnecting the 'rotary reactance and plungers for reciprocating the plungers, said reactance comprising an outer ring, a coaxial inner ring in radial alignment therewith and spaced radially therefrom, a plurality of segmental blocks llttingbetween the rings 'and being, u'

spaced circumferentially thereof to provide operating grooves accommodating the crosspins, and said blocks being arranged one between adjacent pins and being slidable circumferentially of the rings.

3. In a rotary radial plunger pump or motor, a rotatable barrel having a set of circumferentially spaced radial cylinders, valve means for the cylinders, plungers in the cylinders respectively, a rotary reactance eccentric to the barrel, crosspins operatively connecting the rotary reactance and plungers for reciprocating the plungers, said reactance comprising an outer ring, a coaxial inner ring in radial alignment therewith and spaced radially therefrom, a plurality of segmental blocks fitting between the rings and being spaced circumferentially thereof to provide operating grooves for the crosspins, and said blocks being slidable circumferentially of the rings for reducing impact forces occasioned between the crosspins and blocks by changes in the relative speed of rotation of the barrel and rings, and cooperating tongues and grooves on the rings and blocks cooperating' with the crosspins to retain the rings and associated blocks in assembled condition.

4. In a rotary, radial piston pump or motor, a rotatable barrel having radial cylinders spaced axially of the barrel from each other and having their axes in a common plane through the rotative axis of the barrel, valve means for the cylinders, plungers in the cylinders and having their outer end portions spaced apart axially of the barrel, rotatable coaxial reactance rings eccentric to the barrel and positioned respectively between adjacent outer end portions of the plungers and at the outermost end limits of the plungers axially of the barrel, a thrust pin carried by the outer end portions of the plungers and common to said plungers, said pin being operatively connected to all of `said rings for actuating the plungers thereby, means supporting the rings for independent fioating movement axially with respect to each other, and means connecting the outermost end portions of the pin to the outermost end ones of said rings for constraining the end rings and pin to proper relative positions to each other and to the plungers axially of the barrel.

5,. In a rotary radial plunger pump or motor, a rotatable barrel, a plurality of radial flanges on the barrel spaced apart axially of the barrel from each other, said barrel having rows of radial cylinders, the rows being spaced apart circumferentiaily of the axis of rotation of the barrel and each row extending parallel to the axis of 4 rotation of the barrel the cylinders of each row and guided thereby for reciprocation, rotatable,

coaxial, independent reactance rings eccentric to the barrel axis and fitting, with operating clearance, snugly between adjacent faces of the anges and at the outermost faces of the end flanges, re-

'N spectively, thrust pins for the rows of plungers,

respectively, each pin being common to the outer end portions of all plungers in its associated row and to all of said rings, and each of said pins being operatively connected to all of said rings and its associated plungers for actuating the plungers thereby, and means supporting the rings for independent oating and axial movement with respect to each other.

6. In a rotary radial plunger pump or motor, a rotatable barrel, a plurality of radial anges on the barrel spaced apart axially of the barrel from each other, said barrel having rows of radial cylinders, the rows being spaced apart circumferentially ofthe axis of rotation of the barrel and each row extending parallel to the axis of rotation of the barrel the cylinders of each row being disposed in the zones of the radial flanges, respectively, and having their axes in a common plane through the rotative axis of the barrel, said fianges having radial guideways respective to the cylinders, valve means for the cylinders, plungers in the cylinders and having outer end portions disposed in said radial guideways, respectively, and guided thereby for reciprocation, rotatable, coaxial, independent reactance rings eccentric to the barrel axis, and fitting, with operating clearance, snugly between adjacent faces of the flanges and at the outermost faces of the end flanges, respectively, thrust pins for the rows, respectively, each pin being common to the outer end portions of all plungers in its associated row and to all of said rings and each pin being mounted in the outer end portions of all the associated plungers and the rings for rotation about its own axis and relative to the barrel, and each of said pins being operatively connected to all of said rings and its associated plungers for actuating the plungers thereby, and means supporting the rings for independent rotation with respect to each other.

7. In a rotary radial plunger pump or motor, a rotatable barrel, a plurality of radial flanges on the barrel spaced apart axially of the barrel from each other and having radial end faces, said barrel having rows of radial cylinders, valve means for the cylinders, each row of cylinders extending axially of the barrel and the rows being spaced circumferentially of the barrel from each other, the cylinders of each row being arranged at the zones of the flanges respectively and having their axes in a common plane through the rotative axis of the barrel, radial guideways in said flanges and aligned with the cylinders respectively, radial plungers in the cylinders respectively and having outer end portions spaced apart axially of the barrel and reciprocable in the guideways of the associated ange, rotatable coaxial independent reactance rings eccentric to the barrel and respectively snugly tting with operating clearance between the radial end faces of the flanges and between adjacent outer end portions rings for actuating the plungers thereby.

ELEK K. BENEDEK.