US3008423A

US3008423A - Variable capacity, reversible flow hydraulic rotary pump and system

Info

Publication number: US3008423A
Application number: US853776A
Authority: US
Inventors: Eugene J Miller
Original assignee: Individual
Current assignee: Individual
Priority date: 1959-11-18
Filing date: 1959-11-18
Publication date: 1961-11-14
Anticipated expiration: 1978-11-14

Description

Nov. 14, 1961 E. J. MILLER VARIABLE cAPAcI'rY, REVERSIBLE PLow HYDRAULIC ROTARY PUMP AND sYsTEM 4 Sheets-Sheet l.

Filed Nov. 18, 1959 fly-1,. f

E: sa a ATTY,

Nov. 14, 1961 E. J. MILLER '3,008,423

VARIABLE CAPACITY, REVERSIBLE FLOW HYDRAULIC ROTARY P UMP AND SYSTEM Filed Nov. 18. 1959 4 Sheets-Sheet 2 ATTY.

Nov. 14, 1961 Y E. J. MILLER 3,008,423

Y VARIABLE CAPACITY, REVERSIBLE FLow HYDRAULIC ROTARY PUMP AND SYSTEM Filed Nov. 18, 1959 4 Sheets-Sheet 3 /alv l I I 79 1 7, y; INVEN'roR.

E. J. MILLER 3, ,423 VARIABLE CAPACITY, REVERSIBLE FLow HYDRAULIC Nov. 14, 1961 ROTARY PUMP AND SYSTEM 4 Sheets-Sheet 4 Filed Nov. 18, 1959 United States Patent O VARIABLE CAPACITY, REVERSIBLE FLGW HY- DRAULIC RTARY PUMP AND SYSTEM Eugene I.' Miller, 411 Oak Ave., McHenry, Ill.

Filed Nov. 18, 1959, Ser. No. 853,776

11 Claims. (Cl. 103-120) The present Vinvention relates to a variablev capacity, reversible flow hydraulic rotaryy vpump and system, and is particularly concerned withrotary pumps of the vane type in which the capacity of the pump and direction of its flow are adapted to be controlled without changing the direction of rotation of the shaft. v This applicationis a continuation-impart of my prior application of the same title, Ser. No. 705,547, led De-k,

which require variation of the output capacity of a hydraulic system.

An example of the use of such a hydraulic pump is in rotating concrete mixers by hydraulic actuating motors which are driven from the engine of an'automotive vehicle, where the speed of rotation now drops ofI' as the engine of the car slows down.

Another example ofthe use of such a hydraulic'pump is for providing hydraulic uid under pressure for-controlling steering of the car, as the present hydraulic steering controls provide too much 'capacity'at high speed.

and too little capacity at low speed.

Another-.example of theuse of such a pump is in the lCC "FIG. 3 is a vertical elevational view in partial section on axial planes, showing the speed control for a hydraulic system, including the rotary pump of FIGS. l and 2;

FIG. 4 is a View similar vto FIG. 3, showing the parts of the control in the position which they assumeupon zero ilow of the pump;

FIG. 5 is a fragmentary view similar to FIGS. 3 and 4, showing the parts inthe position for flow in the opposite direction; f j

FIG. 6 is a diagrammatic view, showing the hydraulic system and controls for operating a hydraulic motor at -variable speeds and capacities or at constant lspeed and capacity with a variable input, with the parts inthe posil tion of no power output;

FIG. 7 is a similar view, with the parts in the position of rotation of the hydraulic motor output shaft in a counter-clockwise direction;

FIG. 8 is a view similar to FIG. 6, with the parts in the position for clockwise rotation of the output shaft;

FIG. 9 is a view similar to FIG. 8, with the parts in the position which they may assume under control of the governor when operating under the conditions of FIG. 8;

FIG. l() is a top plan view of the elemen-ts of a hydraulic system of the type shown in FIGS. 3-9 with thev rotary pump of FIGS. l and 2;

FIG. ll is a view in'perspective of the movable compressor chamber used in the pump of FIGS. l and 2;

hydraulic dfve 'of any mechanism, including the driving wheels of an automotive vehicle'.

Another object ofthe invention is the provision of an improved hydraulic pump control system including such( a variable capacity pump and 'suitable speed controls for controllingl the output of the pump and maintaining its ow and capacity constant at variable speeds or suitably varying its capacity and pressure at constant speeds of drive.

Another object of the invention is the provision of an improved variable capacity rotary pump of the vane type adapted to be used for compressing gases or liquids and a system for controlling the same which is simple in construction, capable of economical manufacture, constant,

and positive in its performance, and adapted to be used for a long period of time without necessity for' repair or replacement of its parts. Another objecty of the invention is the provision of an improved variable capacityvrotary pump of the vane type in which all of the connections for fluid or-fluid conduits may -be provided with rigid piping, as distinguished from the: useV of exible conduits because the maintenance of uid-tightjointsis more easily and economically accomf` plished by jusing rigid piping. 1 y I i Other objects and advantages of the invention-wrll be FIG. l2 is a view in perspective of the rotor of the rotary pump. v Y.

Referring'to FIGS. 1 and 2, 20 indicates the housing of the hydraulic pump in its entirety, embodying the in` vention. The housing 20 may consist of` two parts 1'8 and 19 forming a housing with aV lower stable base 21, supporting an upper enlargement'ZZ', which is provided with a substantially rectangular chamber 23.

The chamber 23 may have upper and lower' plane inner walls 24 and 25; and its

lateral plane walls

26 and 27 are provided' by a pair o-f side-

plates

28 and 29. Thus the upper enlargement 22 of the pump housing may haveV a through rectangular aperture forming a chamber 23, with the

side plates

28 and 29 closing the ends of this aperture. f

The

side plates

28 and 29 are adapted to be vreceived in rabbeted recesses 30 and 31; and the-side=plates are provided with complementary rectangularfformations 32' through bore 39 and i401 for passing the rotor shaft 41;`

and the bores 39 and 40y have counterbores 42 and 43 for receiving the =ball, bearings 44, which in each case include an inner race 4S, an outer race 46, and balls 47.

Each counter-bore 42,- 43 may have a snap ring for securing the outer races in the counterbore; land each apparentirom the -following'description andthe accom-M f panying drawings, in :which similar" characters of refer-.

ence-indicate similar partsthroughout theY several views.

Referring to the drawings, of which there are'- four:

sheets- 5 FIG. 1 lis a vertical-axialsectional View, taken on the plane of the line 1 1, lookingV in the direction, of the arrows, of FIG. 2; f p i l FIG. 2 is a vertical sectional view, taken on the vplane of the line 2-2 of FIG. l, through the rotary pump;

' 51 to enclose the oil seal.

counterbore may have an oil seal, comprising a leather seal 48, having a cylindrical flange and a radial flange and-'a coil spring 49 holding the seal against the shaft; and a suitable closure plate 50 may be bolted to each hu Thepump housing 20 is provided in its chamber 23 with a movable pump block 50, having a central portion which is rectangular in shape and provided with upper and

lower plane walls

61, 62 and with the lateral plane walls 63, 64 so that the Iblock 60' may be slidably mounted in the .block 60 and chamber 23, which permits the block 60 tegral with the block 60, arid each of which is guided in 5 opposite sides of the rotor.- Y v a

cylindrical bore

69, 70 communicating with the rec- Each vane 103 comprises a rectangular'plate'having tangular chamber 23. Each cylindrical extension 6 7, 68 plane surfaces on itsj opposite sides and endsfandi'nner has an integral tubular cylindrical extension 71, 72 which edge for slidably engagiriginV the'groovesj109vvith miniis slidably mounted in a

cylindrical bore

73, 74; and each mum leakage and" fo'r'sli'd'ably l engaging"the'end walls tubu-lar extension has a

tubular bore

75, 76, and is pro- 10 26, 27 on the inside of th'eplates 28,29.A

vided with a threaded end portion 77, 78 (FIG. 1l) for Each Vane has its outer edge 113 beveled to provide attachment of rigid tubes adapted to carry oil under a line Contact with the cylindrical wall of the pumping-- Compression, chamber 100; and the vanes 1,03 engage the walls ofthe Each of the

cylindrical bores

69 and 70 is long enough chamber 100 -at all times, the slots of the rotor sliding to receive the

cylindrical extensions

67 and 68 of the 15 on the vanes. block 60 with a clearance, leaving

spaces

79 and 80 at Keeping the vanes at constant radial position `also per` the ends of the bores 69 and 7% for receiving oil under mits higher speed operation. compression to actuar@ the block from left to right The rotor has neoprene plugs 1Min Slots V110 toabsorbrg and vice versa. shock and differentials of pressure, which causeheating The oil inlet or outlet bores 81 and S2 extend` into 20 0f Oil- A'SCleW bolt may hold each plugin ,its slot. the housing 20 and communicate with the spaces 79 and The

Oil relief gfOQVes

101, 102 a110W Oil tQfllHl head` 1 for admission or outlet of oil under pressure; and the 0f the Valles; and gIOOVeS 101, 102 are absent algthe Seal bores 81, 82 have threaded counterbores 83, 84 forreareas 16, 17, which are la little Wider than the vane space ceiving the

rigid oil conduits

85, 86. Width.

The

cylinders

67 and 68 have their cylindrical walls 25 The Operation 0f the purnp is as follows. y provided with peripheral grooves 87, SS for providing When the Parts 0f the Pump, and i11 Psitielllal' the `space for the O rings 89, of neoprene, which project block 60, are lil the Positiefi 0f FIG 6, OCeUPYil-ig Posi-k from the,

grooves

87, 88 sufficiently to maintain Gip/[ight tion half way between the lateral walls of the cylindrical I engagement with the

cylindrical bores

69 and 70.

Chamber

100, 110 Oil is Pumped ill either difeetidtl- The cylindrical extensions 71 and 72,Y forming conduits 30 when, the block 60 is itl the Position VOf-FIG l,

y'diie

75 and 76, have partially circular grooves 91 and 92 for i Pumping Space 115, in advance 0f the 1'0t01' 105 and Valle y receiving O rings 93 and 94 of neoprene, which project 103, rotating eeuntel'eleekwise, is adapted t0 13e diminished i from the grooves sufficiently to provide a liquid-tight conill ,Size as the Vane 103 PrOgfesseS and t0 Pump Qll Out tact with the eounterbores 73,7 74, of the conduit 75. The opposite space 116 increases Block 60 is provided on each of its lateral surfaces 35 Size, but Pumps 110 Oil because it'iSv Closed at theoutlet with a partially circular groove containing a neoprene Conduit 76 and iS Het Previded Withtlle' Oil relief 0 ring 15, which itself is cylindrical in section and circular groove 101- y Y y in elevation, sealing the block about the rotor inthe cavi- Oil lis suckedln at the Conduit 75, Which is en inlet at ty 61' this time; and oil is pumped out o f the conduit76.v

Thus the conduits connected at 83; 84 may be usedto 40 Whedthe PaltS are in the Position 0f FIG- 8 iliebloek provide oil under pressure .to the

spaces

79 or 80 t'o move 60 1s 'at lts leftposltloll and the TQtO' 10`5} 1'9ttltll1g1i.1 1'tll,e,Q the block 60 back yand forth, the purpose of which is to I sdm? direction, PUIHPS Oil Out ofthe-Conduit 75 and sucksl vary the capacity of ow and its direction of oil pumped oil m at the onduit 76- v from the compresson A t a position `such as thatin 9, wherethe block f The tubular bores 757 76 communicate with a Cyn-np 4 5 60 is somewhat to the left of a centralposition, the oil tical pumping hmber 100 in the block mh extendig flow. out of the right hand conduit 75 is diminished in,kv from side to side and closed by the side plates 28' and i amount dependmg 011 the Position Off the r0t0r`il1 iS 29. The chamber 100 may be cylindrical in shapeso chamber 100; y U that the vanes move in a circle lat all times and are'urgedy the dlfectmn and eap'fclty 0f the Oil at the COU- outward by centrifugal force. The purpose ofl the cy- '50 dal? 75 31191.75 may lie Varied at vWill bY'Ve-i'ying .tile lindrical chamber shape is to reduce vane wear, or vane Posltlon of 'block 60 With the fowl: constantly Total chatter caused by uneven circumference in vane pumps mg at the? same Spel-5d m the Same dll'eetloll of the prior an Referring to FIGS. 6 -9, these are diagrams of a suit-H Each of the lateral ends of pumpg ChamberV 10a-m33, able control forV providing the oil under pressure for'the be provided with

oil relief grooves

101, 102 comniunicat- 55

Spaces

79 and 80 *at the, ends Offhe block 6010 mQVe ing with the

bores

75, 76 to permit the oil to be driven .block 601mm 'left to .right 'or Vll Versa or to hold' :it i out of the @amber k by the

vanes

103, 104 carried by m the fixed Central Posltonr. i

p c Y 1 on w ere `eroo11v The rotor vanes 103 are preferably made of magnet- 105 pumps, no on because its

umping spaces

115 ,116, izable metal, such as steel, having poles at the inner and 60 are always of the same size outer ends of the blades, which are'attracted outwardly In addition t the pump- 05u16 diagram Showgond t 0 the Walls O f bere/100 edd heldin eenstaliteontaetwlth 76 communicating through conduit '127"witl1` the yinlet trie bore 100 by magnetic attraction. The rotor maybe 12!) of a hydraulic motor ,121 of the gear type; havinga. Iliade ef manganese 0r aluminum, lVHICh 1S 110t Paie' e5 pairof pumping gears' 122, `123fmeshing with eachother i magnetic, and the

sideplates

28, 29 may be of 'bronze, and'slidably rotating in the communicating partially cylinfr t thus eliminating magnetic attraction in other directions dricalch'ambers-124,Y 125,L so that the'V oilv entering into` so that a constant seal is effected with the `bore"'100` `tooth spaces is not'carried-aroundfrominlet 126't'oconf without springsand without radial movement'of thel duit 127. vanes, 70 Conduite 127 and 127a preferably lead to pressure The rotor 105 may form an integral part of the shaft f 41 or be keyed thereto andis a cylindrical body provided 4 f v the vanes 103, which are pressed outward by centrifugal force.

The slots 109 do not extend through the shaft 41 for the reason that there are differentials of oil pressure on equalizing chambers 128,` `which`have'oil`129 under com pression by means'of 'aerated lneoprene 'balls'"1'30 "ofi foamed neoprene covered with a skin ofneoprenefthe oil being supplied thi-oughta valved 'conduit '132, to V'charge the system.'y Y

with plane ends 106 and 107 'and a cylindrical outer surface 108. The rotor 105 FIG. l2) has v-a multiplicity of axially extending slots 109- (eight) `for slidablyr'eceiving'"

Conduits

85 and 86, extending from thespace's 79 and 80 at the ends of the block, communicate with the cylinders 134,135, which are'movably mounted on a frame 136 under control of the governor 137. The

cylindersv

134, 135 may be in the form of a ram provided with pistons 138, 139l controlled by

piston rods

140, 141.

In FIG. 6 the

pistons

138, 139 are in intermediate posi- 4tionto -hold the block 60 in intermediate position for no ow and no pressure.

Referring to FIG. 3, this is an elevational view in partial section, showing the governor construction, in which the governor 137 and its associated parts are mounted upon a base-138. The base 138 has a column 139 at one end, supporting a fixed shaft 140, with its reduced end in a ybore 141, where it is secured by a nut 142 on its threaded end 1'43, clamping the annular shoulder 144 against the end of hub 14S.

The -xed shaft 140 has an elongated cylindrical body 146 rotatably supporting a driven pulley 147, having a V groove 148 for receiving a V belt; but the pulley 147 may be replaced by a gear inthe case of a geardrive. The V pulley .147 may have an elongated hub 149 with a bearing bore 150 rotatably mounted on the shaft body 147 and conned against axial movement by the head 151.

` The elongated hub 149 has a sliding governor collar 152 which is provided with a peripheral groove 153 for receiving the ends 15'4 of the governor control weight levers 155.4 These levers have enlarged masses 156 extending toward the V pulley 147 from the pivots 157 so that the masses are pivoted on the lugs 158 and tend to y outward due to centrifugal force as the speed of rotation of the pulley increases.

f The collar 152 has a groovev for receiving a spline 159 on hub 149, engaging in groove 160 so that the collar 152 slides on hub v149, but rotates with it. Collar 152 supports a thrust ball bearing assembly 161, comprising an inner race 162 of angular shape with the ball groove 163; and a snap ring l164 in groove 165 holds the race 162 againstannular shoulder 166.

Athrust ball bearing housing z167 has a cylindrical chamber 168 provided with a counterbore and annular shoulder 169, engaging the outer race 170, which in turn is angular inshape and provided with groove 171, and is held in place by a snap ring 172 in a suitable groove.

'Ihe balls 173 in the ball bearing assembly are subject to axial thrust and permit thethrust bearing 167 to stand s'till, while the collar 152 rotates in it and exerts axial thrust. n n g Thrust bearing housing 167 has a base plate 174, to which is bolted the base plate 175, supporting the ram cylinders 134 and'135. The ram cylinders have inletoutlet conduits communicating with the cylinders at 176 and 177 and connected to

conduits

85 and 86.

,The ram pistons are'shown at 138,v 139 and the piston rods at v,140, 141. n Y n 'Cen trifugal f orce acting on the

governor weights

155, 156 is resistedby a coil'spring 178 having one end hooked in an eye 179 carried by plate 175; and the other end is hooked in an aperture180 carried by threaded rod 181. Threaded rod 181 is provided with a hand nutV 182 and passes through an Unthreaded bore 183- in column 184.

.Rod 1 81 has a head 185 to be held while the nut 182 is tightenedor loosened to adjust 'the tension on spring 178. The amount of Ytension ofspring 17 8 determines'the point atwhich the cylinders v131, 1314 are moved toward the right for relieving the pressure on the oil in the cylinder space v186, which in FIG. 3 iscontrolling the position of blo`ckf60 by forcing/oil under pressure through conduit 86 into` space 80, urging theblock 60 toward the right into the position of FIG. l. f

By relieving the pressure on oil in space 186 of ra cylinder 1.34.` the block 60 is permitted to move slightly towardthe left in FIG. l, reducing the capacity output of 'the pump in response to the action of the governor 6. weights 155, which move the

plates

174, 175 and the

ram cylinders

134, 135.

The tension of spring 178- may be so regulated that a substantially constant output is maintained at the output conduit 75 of the pump 20.

In the embodiment of FIGS. 3-5 oil under pressure is maintained in only one of the

spaces

79 or 80; and in FIG. 3 it is the space 80 which is subjected to oil under pressure by ram piston 138, the piston rod 140 of which is held in the position of FIG. 3 byY engaging the end of a sliding rod 187 in tubular guide 188 carried by column 189.

Rod 187 is Iheld in xed position in FIG. 3 by control lever 190 pivoted at 191 on the lug 192, and having its handle 193 secured in a notch or groove 194 in the holding segment 195, which has additional laterally

open notches

196 and 197. Holding segment 1=95 is mounted on column 189 and extends adjacent the path of handle lever 193, which is resilient; and the handle 193 must be bent laterally to get it out of one of the

notches

194, 196, or 197.

' In FIG. 3 the handle 193 is in the proper position ttor the pump to pump oil under pressure out of the conduit 76.

The other end of lever 190 has a pin and

slot connection

198, 199 to a sliding rod 200 in tubular guide 201 carried by column 189.

VRod 200 may bel positioned to engage the end of ram 141; but in FIG. 3 the rod 200 is free of the ram rod 141 by a clearance at 202 in the guide 201; and the cylinder 135 and piston 139 are exerting no pressure on the oil in space 203, which communicates by conduit 85 to the space 79 on the right of the block 60 in FIG. l. -Thus the pressure in the space 79 at the right of the block 60 is relieved, and permitting-the pressure ini space 80 to hold the block 60 in the right hand position of FIG. 1.

Referring now to FIG. 4, the handle lever 193 isv there in an intermediate position in the groove 196,-with both the rods in the position of FIG. 4, where the rodv187 engages the end of piston rod 1140 and rod 200 engages the end of piston rod 141.

The

pistons

138 and 139 in FIG. 4 are in an intermediate position in which there is an equal amount of oil under pressure in space 186 and space 203 in the cylinders. The block 60 is then in the intermediate position of FIG. ,6, whereA block 60 attains its own neutral position by so moving that it pumps no oil. The pump may run at 0 to 1000 r.p.m. without radial movement of vanes.

The connection of rod 187 to lever 190 is by a pin and

slot

204, 205 because the sliding connection is necessary between the pivoted lever and the sliding rod.

Referring to FIG. 5, this is a 'fragmentary View, showingA the

ram pistons

138, 139 in the position of FIG. 8, where the rotor 105 engages the right side of the pumping chamber and the conduit 75 becomes the outlet of the pump, with the conduit 76 acting as inlet.

The governor controls the amount of oil under pressure, which forced into the space 79, urginlg the block 60 toward the left, and regulating the size of the

compression spaces

115, 116.

In FIG. 5 the handle lever 190 has its handle located in notch 197 (not shown -in FIG. 5); and the ram 134 would be inactive'because its piston lrod 1240v would be out of engagement with rod 187.

FIG. 9 shows a position of the block 60 in which the block 60 has been permitted to move toward the right slightly from the position of FIG. 8 to reduce the output in conduit 76 responsive to the action of the governor.

In FIGS. l-5 the governor` pulley 147 is driven by a belt connected to the pulley of the output iluid motor at shaft 206 so that the governor speed of rotation depends on the speed of the output motor 121.

Referring to FIG. l0, this is a top plan view of one form'of hydraulic drive, including an electric motor 207 121, and governor 137. The prime mover 207 drivesthe pump by means of pulley 209, V belt 210, and driven V -pulley 211 on compressor shaft 41.

The pump is connected by the conduits S5 and 86 to the

rams

134, 135, which are `governed by the governor 137. The pump 2t) is connected by conduits 127 and 127e through the surge tank 123 to the liuid motor 121 at inlet-

outlet

120, 126. Fluid motor 121 has a power outlet pulley 212 engaged by driven belt 213 for driving any kind of equipment, such as a power steering equipment, a concrete mixer, or the drive wheels of an automobile, or the oil may actuate ramsY of a dump truck.

The operation of the system is as follows: The rotor 105 of, the pump 20 is held, except ifor rotation, in the same position in the pump 20 by the bearings 44; but the block 60 with its pumping chamber 100 may move relative to the rotor. to the positions shown in FIGS. l or 6-9 to vary the direction or capacity of the fluid pumped by thepump.

The pump block 'with its pumping chamber 100 is moved to the right or left by oil under pressure in the

spacesV

65 or 66; and this oil under pressure is supplied by the

rams

134, 135, which provide oil through the

conduits

85, 86 for moving the block 60 back and forth, causing it to pump, with its outlet at conduit 75 in FIG. 7, or to pump with its outlet at 76, in FIG. 8.

The `rams 134, 135 and

spaces

65, 66 and the connecting conduits have a suitable supply of oil inthem, which is under pressure when the ram rods 140 vor 141 are positioned to exert pressure.

When the

ram rods

140, 141 are in the intermediate position of FIG. 4 or FIG. 6, the block 60 is free to move by internal pressure to the central positionof FIG. 6; and the rotor 105 is centered in the pumping chamber 100, so that the pump pumps no oil in either direction.r

When the block 60 is in theV position'of FIG. 8, the cond-uit 75 becomes the outlet conduit of the pump and the fluid motor 121 is driven in the clockwise direction. Whenv the system is operating with either of its conduitsV 75 -or 76 serving as' outlet, thek output or capacity of the pump is maintained constant by the governor 137 so that the prime mover 2 7 may operate at a Variable speed, while the output of the iluid motor 121 is maintained constant by the governor 137.

It will thus be observed that I have invented an improved hydraulic pump which is adapted to have its pumping chamber moved relative to itsv rotor so thatV it may pump hydraulic fluid in either direction or may reduce its output to zero, while constantly rotating in the same direction, or its output may be varied in capacity while the pump shaft is constantly driven in the same direction at the same speed;

Mypump and pump system may be employed on trucks to be driven by the truck engine to provide hydraulic power for actuating the rams, which control -the tilting of the dump'body, or for driving concrete mixers, or for driving the drive wheels of the vehicle or power steering.

While I have illustrated a preferred embodiment of my invention, many modifications may be made without departingfrom the spirit of the invention, and I do not wish to be limited to the precise details orf construction set forth, but desire to avail myself of all changes within the scope of the appended claims.

Having thus described my invention, what I claim as S new and desire to secure United States, is: Y i

l; A variable capacity; pump of the vane type, come` prising a supportingk housing having'a rectangular charnbe'r provided'with plane bottomV surface,` plane topsurface, andplane side surfaces on side plates, apurnphous-` ing block shorter than said chamber, and having planetop, bottom, and side surfaces engagingl the walls of. said chamber for sliding movement of A said block in said"Y housing, said block having a cylindrical rotor chamber with its axis extending from side surface to side surface of said chamber in said block, said -blockhaving. a rigid cylindrical `block extension at each of its opposite ends, and each block extension` being slidably mounted in a cylindrical extension chamber of `said rectangular chamber, said block having a smaller cylindrical iconduit extension extend-ing from each blockl extension and slidably mounted in a cylindrical bore in each end of said supporting housing and defining liquid; pressure chambers about each conduity extension at each end of said block, a rotor in said rotorV chamber, and comprising a cylindrical member and a supporting shaft rotatably mounted in bearings carried by said side'plates, of said supporting housing, said shaft beingl centrally' mounted in said side plates; and said rotor beingi cylindrical and smaller in diameter lthan the :rotor chamber, but extending from end to endof the rotor chamber into engagement with the plane surfaces of said side plates, the said block' having a range of movement insaid supporting housing longer than needed to. cause the rotor 4to engage the rotor chamber at eitherend` of. the block movement, said rotor chamber having dia-v metrically oppositely located inlet-outlet ports, and' a conduit extending from each of said` ports inthe block extensions and conduit extensions at eachl endV ofthe block, a multiplicity of vanes located between the inlet-outletl ports on' each side* of the rotor; said vanes extending the full lengthv of said rotor and slidablymounted in complementary radial slots in saidrotor to be fully housed in the rotor slots with a clearance at the base of each vanewhen each vane is in the position to engage and pass one of said inlet-outlet ports, said vanes being mounted for freesliding movement, to be` held radially outward in engagement with the cylindrical' wall of the rotor chamber by centrifugal force, the varies rotating in a constant radial position by engagement with the cylindrical walls of the rotor chamber.-v and rotation of the Varies on the axis of the rotor chamf: ber at all times to eliminate vane chatter, saidrotor and the walls of the rotor chamber establishing -a rotorseal at the leadingedge of one inlet-outlet port and the vanes establishing a seal with the rotor chamber wall constantly with a compression chamber decreasinginsize toward the rotor seal and a suction chamber increasing in size away from the rotor seal,I Athefsaidrotor chamber having in` its peripherytapered oil relief grooves tapering away from each pertain opposite directions, and the-grooves ending Vwith their small ends; at a point spaced from the inlet-outlet ports, which space is substantially equal torthevspacing between two vanes, to provideV a pumping zone only beyond the tapered ends of said grooves;

2. A variable capacityfpump according to claim 1, in lwhich the block extensions and' conduit extensions have peripheral grooves in theirk cylindrical surfaces'with resilient U rings substantiallyA housedV in, butA projecting from, the grooves to estabiisha seal on both end s of the liquid pressure chambers, .andthe rotor has a groove dening a circle in each of the rotor ends, said'latter groove containing a resileint O ring, engaging -the plane surf-aces of the side wal-ls of the rotor chamber.v

3. A variablecapacitypump according'to claim 1, in which one `liquid pressure chamberatv one end of the block is hlled with liquid under-pressure. and connected by a by Letters Patent of the 9 conduit to a cylinder having a manually controlled piston for urging the block into rotor sealing position.

4. A variable capacity pump according to claim 3, and a centrifugal governor driven by the pump output and urging said latter cylinder in a direction to relieve pressure at the rotor seal upon increase of the output pressure.

5. A variable capacity pump according to claim 1, in which the rotor has peripheral recesses between `each pair of vanes, the recesses containing a shock absorbing compressible solid, to absorb pressure impulses when a hydraulic fluid is being pumped.

6. A variable capacity pump of the vane type, comprising a supporting housing having a rectangular chamber provided with a plane bottom surface, plane top surface, and plane side surfaces on side plates, a pump housing block of paramagnetic material, shorter than said chamber, and having plane top, bottom, and side surfaces engaging the walls of said chamber for sliding movement of said block in said housing, said block having a cylindrical rotor chamber with its axis extending from side surface to side surface of said chamber in said block, a rotor in said rotor chamber, and comprising a cylindrical member and a supporting shaft rotatably mounted in bearings carried by the side plates of said supporting housing, said shaft being centrally mounted in said side plates, and said rotor being cylindrical and smaller in diameter than the rotor chamber, but extending from end to end of the rotor chamber into engagement with the plane surfaces of said side plates, said block being movable in said housing in either direction suiciently to permit the cylindrical surface of said rotor to engage the cylindrical surface of the rotor chamber at either end of the range of movement of the block to effect a seal between the ro-tor and the rotor chamber at either end of said range of movement, said rotor chamber having diametrically oppositely located inlet-outlet ports at each end of the block where the rotor effects a seal adjacent either inlet-outlet port, a multiplicity of magnetized vanes slidably mounted in the rotor and extending radially thereof and located between the inlet-outlet ports on each side of the rotor, said vanes extending the full length of the rotor and being slidably mounted in complementary slots in said rotor to be fully housed in -the rotor slots with a clearance at the base of each vane when any vane is in the position to engage and pass one of said inlet-outlet ports, said vanes being urged outward into engagement with the cylindrical wall of the rotor chamber by centrifugal force and magnetic attraction towards said cylindrical wall, and the vanes rotating with the rotor in constant engagement with the cylindrical walls of the rotor chamber, the vanes rotating on the axis of the rotor chamber at all times to eliminate vane chatter and vane movement except rotation, said rotor and the walls of the rotor chamber establishing a rotor seal at the leading Edge of one inlet-outlet port, and the vanes establishing a seal with the rotor chamber wall constantly, with a compression chamber decreasing in size toward the rotor seal and a suction chamber increasing in size away from the rotor seal, said rotor chamber having in its periphery tapered oil relief grooves tapering away from each port in opposite directions, and lthe grooves ending with their small ends at a point spaced from the inlet-outlet ports, which space is substantially equal to the spacing between two vanes, to provide a pumping zone beyond the tapered ends of said grooves.

7. A variable capacity pump according to claim 6, in which the rotor is provided with a V-shaped recess in its cylindrical surface between each pair of blades, the reces-s being iil-led with co-mpressible resilient material for taking up the pulsations of pressure and producing an even ow.

8. A variable capacity pump according to claim 6, nclu-ding means for urging said block in one direction inside said housing to establish a seal with said rotor and determine the direction and amount of volume of uid delivered by said compressor.

9. A variable capacity pump according to claim 6, in which the compressor block may move to a central position with zero capacity output or to either end position, the rotor rotating in the same direction in all said positions.

10. A variable capacity pump according to claim 6, in which the block has a cylindrical extension sliding in a longer complementary cylindrical extension in said guiding chamber, and having an end surface subject to uid pressure in a fluid chamber in said latter extension, to move the block to vary the relative position of rotor and rotor chamber to change the capacity of output.

11. A rotary vane pump according to claim 6, in which the cylindrical block extension and the rigid conduit extension have peripheral grooves containing 0 rings of neoprene to effect a fluid seal.

References Cited in the iile of this patent UNITED STATES PATENTS 800,023 Sharpneck Sept. 19, 1905 1,160,032 Allan Nov. 9, 1915 1,486,682 Phillips Mar. 11, 1924 1,593,498 Kuhn July 20, 1926 1,706,739 Moran Mar. 26, 1929 2,031,749 Vincent Feb. 25, 1936 2,080,810 Douglas May 18, 1937 2,135,881 Wentworth Nov. 8, 1938 2,177,097 Doe et al. Oct. 24, 1939 2,179,071 Wiedmann Nov. 7, 1939 2,249,059 Stenger July 15, 1941 2,291,011 Vickers July 28, 1942 2,356,916 Brewster Aug. 29, 1944 2,588,342 Bidwell Mar. 1l, 1952 2,888,806 Teumer June 2, 1959 2,931,177 Teumer Apr. 5, 1960