US2621019A - Hydraulic jack - Google Patents

Description

Dec. 9, 1952 J. J. MUELLER 2,621,019

HYDRAULIC JACK Filed March 12, 1945 5 Sheets-Sheet l IN VEN TOR.

kja a e pfa Jjl/wlefi J. J. MUELLER HYDRAULIC JACK Dec. 9, 1952 Filed March 12, '1945 5 Sheets-Sheet 2 Dec. 9, 1952 J. J. MUELLER HYDRAULIC JACK Filed March 12, 1945 5 Sheets-Sheet 5 J. J. MUELLER Dec. 9, 1952 HYDRAULIC JACK 1% A [q Q W LP \mm\\\ 9% g Filed March 12, 1945 Patented Dec. 9, i952 UNITED STATES PATENT OFFICE HYDRAULIC JACK Joseph J. Mueller, St. Joseph, Mich., assignor to Auto Specialties Manufacturing Company, St. Joseph, Mich, a. corporation of Michigan Application March 12, 1945, Serial No. 582,281

v 4 Claims.

This invention relates to what are known as floor jacks.

Among the objects of the present invention is to provide a jack of the present construction which is composed of a minimum number of parts, many less parts than commercial jacks of this general type which are now on the market.

Another object of the invention resides in providing a simplified means for actuating the high pressure pump cylinder from the handle mechanism in a plurality of adjustable arcuate segments all of which lie in a common plane.

Another object of the invention is to provide an improved floor jack having elongated handle means for actuating the high pressure pump cylinder and also for actuating the pressure release valve which permits the liquid to return from the ram cylinder back to the reservoir, wherein simple means is provided for detachably removing said handle from the mechanism which it actuates, and particularly wherein when the handle is so removed the relief valve will be inaccessible for operation so that the jack cannot be inadvertently lowered.

Yet another object of the invention resides in providing a construction wherein the ram cylinder and ram, the high pressure pump cylinder and piston, and the pressure relief valve and its actuating mechanism are all in a common plane centrally of the ram cylinder, thereby enabling the use of but one universal joint connection between the pressure relief valve mechanism and the reciprocating handle which conjointly operates the high pressure pump piston and the high pressure relief valve, in one case by a reciprocating movement and in the other case by a turning movement.

Another object of the present invention is to provide a spring pressed ball release valve in the ram cylinder chamber which is operable when the pressure gets too high in the ram cylinder chamber, to open the valve and permit the liquid under pressure to return back to the reservoir.

Another object of the present invention is to provide a floor jack having a ram cylinder and ram disposed in substantially horizontal position with respect to the floor when the jack is in operative position and wherein the high pressure pump cylinder and piston and the pressure relief valve and its operating mechanism are disposed at an angle of substantially thirty degrees with respect to the horizontal, thereby providing a much more simplified construction of floor jack, whereby a number of parts of the floor jack may be eliminated, including an extra universal mechanism between the relief valve and the handle operating mechanism, and whereby also the parts are accessible from a standing position of the operator.

Yet another object of the present invention is to provide a floor jack having mechanism providing a relatively slower power lifting pump and a relatively faster or speed pump constructed and arranged so that when lifting the liquid-carrying member of the jack up to the load, both the power pump and the speed pump are operative, speedily to move the load member up to the load engaging position and thereafter the power pump only operates and the speed pump automatically cuts out.

Yet another object of the invention resides in providing a combined power or pressure operating pump with a speed or accelerating pump, which are operable quickly to get the loadcarrying member up to the load and thereafter the mechanism is operable to lift the load by the power pump alone, the speed pump automatically cutting out, and this mechanism is operable irrespective of whether it is on a floor jack or any type of hydraulic jack suitable for its adaptation.

Yet another object of the invention is to provide an hydraulic jack having both a speed pump and a pressure pump combined as one single pumping mechanism, together with automatic mechanism for cutting out one of the pumps after the load has been engaged.

These and other objects of the invention will be apparent from a perusal of the following specification when taken in connection with the accompanying drawings, wherein:

Figure 1 is a perspective view of the improved floor jack as it appears from the operating end;

Figure 2 shows perspective views of the associated parts of the jack; i I

Figure 3 is a partial plan sectional view" taken on the line 33 of Figure 4;

Figure 4 is a longitudinal section line 4-4 of Figure 3; I 4

Figure 5 is a sectional view of the left portion of the jack with the load-lifting member in raised position;

Figure 6 is a right hand end view of the jack with the handle port-ion broken away and a portion being shown in cross section;

Figure 7 is a sectional view showing an enlarged cross sectional view of the right hand portion'o'f the jack, showing the operating mechanism and taken on line 1-! of Figure 3:

Figure 8 is'a perspective view showing associated parts of the lifting mechanism;

taken on' the Figure 9 is a plan section taken on the line 99 of Fi ure 7;

Figure 10 is a lon itudinal enlarged sectional view of a modified tyoeo f high pressure pump, taken on the line I9I 6 of Figure 11;

Figure 11 is a view taken on the line IIII of Figure 13;

Figure 12 is an enlarged diagrammatic view showing the outline of the valve containing member in dot and dash lines, the valves and in erconnecting passa ewavs being shown in full lines, to more clearly show their association with each other: and

Figure 13 is a plan section taken on the line I3-I3 of Figure 10.

Referring now to the drawings in detail. the jack comprises a chassis shown particularly in Figure 2, which includes an enlarged body section formed of the two vertically disposed side plates 2 and 4 which at the forward end are joined by a top plate 6 having a forward and downward inclination. This top late 6 has two rearwardly extending ears 8 and Ii! s aced a art and provided with registering perforations I2 and I4 for the reception of a pivotal pin I6 hereinafter described. That section of the body portion to the rear of the top portion 6 is open at the top. At this point the two side plates 2 and 4 are united by a rear transversely dis osed wall I4 which in turn has a arallel extension in the form of vertical walls I5 and I8 and which are rigidly and inte rally connected as at .26 by a top bridge portion for rigidity. These vertical side walls I6 and I8 are interconnected as at 22 by a transverse integral web which has a depressed cup-like cross groove 24 formed at the top thereof and the rearmost portion 26 of the body portion 22 is provided with registering openings for the reception of a stationary axle 38. A threaded pin 32 holds the axle 3D in osition on the chassis 26. The opposite ends of the axle carry stationary shields 36 and 38 wh ch are pinned thereto as at 39 and 40 and casters or wheels 42 and 44 are rotatably mounted on the opposite ends of the axle 30.

On the underside, the bodv of the chassis is provided with two downwardly depending webs 46 and 48 for urposes of ri idity, and these webs are provided with registering a ertures which extend parallel to and on the longitudinal axis of the chassis. At the larger end of t e chassis the underside the eof is provided with downwardly depending partitions 5!] and 52 which provide a mounting for the ram cvlinder as shown in Fi ure 4. In other words, the underside of the chassis is s bs antially hollnw exce t for certain of the rigidifying webs 66, 48, 58 and 52. The larger end of the chass s is provided with two integral outstanding shoulders 54 and 56 each of which is provided with a vertical bore vrotatably to receive the t rnable pos s 58 and 66 of a caster wheel a sembly com rising the ball bearing mounting 62, the front shield 64 on which are mounted the axle 66 and the rotatable caster 68. Means such as a pin ID serves to hold the rotatable shank 58 of the casters in position on the shoulders 54 and 56, permitting them to rotate but preventing their withdrawal.

The larger end of the chassis body below the top 6 is formed as a vertical flat front plate I2 carrying the relatively large opening or bore I4 in line with the high pressure pump cylinder hereinafter referred to. In addition this plate 12 is provided'withthe fourspaced apart-threaded bolt holes I6, which are adapted to receive the bolts which bolt on that part of the hydraulic unit 82 in which the high pressure pump cylinder, the pressure relief valve, and the various ball controlled liquid passages are formed. As shown in Figure 2, this high pressure pump cylinder head or unit carries affixed to its the ram cylinder 84 and its projecting ram 86. As shown clearly in Figure 7, the ram cylinder 84 snugly fits and lies within the webs 50 and 52 which depend downwardly from the top portion 6 of the chassis. The head or unit 82 includes the integral vertical plate member I5 from which the ram cylinder 84 projects. When the bolts 80 are tightened the vertical plate 15 of the head 82 is snugly tightened against the flat face I2 of the chassis, the ram cylinder 84 projecting into the opening 14 of this end of the chassis.

A load-lifting carriage, hereinafter described, is mounted upon the pivotal pin I6 which passes through the perforated ears 8 and ID of the chassis body 6 and also through a cross bore 96 of a downwardly extending section 98 of the loadlifting member. This member has two side flanges I6!) and I62 which carry spaced apart bearing bores I64 and IE6 adapted to receive a pin I68 which carries a roller H0. The elongated load-lifting and lowering carriage 88 is shown in Figures 1 and 2. It is provided with two vertical sides 90 and 92 and the transverse top 94. The forward end of this load-carrying member 94 is provided with two outstanding ears H2 and H4 which are perforated as at H6 and I I8 to receive a pin I26 which supports a load lifting head I22. This head has a centrally disposed annular flange I24 receivable in a centrally apertured disc I26 the apertures of which receive the flange I24 of the load lifter I22 whereby the load lifter I22 may rotate as desired. The flange I26 is provided with two spaced apart ears I28 and IE8 which are supported by the cross pin I26. In addition, the flange I26 carries two lateral toes I32 and I34 which receive a pin I36 connecting to links I38, I39, the other ends of which are pivoted as at I40 to the side plates 2 and 4 of the chassis body. The purpose of these latter links is to maintain the rotatable work holder I22 in constantly horizontal position. When the load is in lowered position it will rest within the grooved cross slot 24 of the chassis, thereby enabling it to nest in compact relationship.

A plunger I42 is supported by the member 98 as shown in Figures 3 and 4, and seats against a shoulder 5 .4 which is pivotally mounted on the pin I88. The plunger I42 is surrounded by a coil spring I46 and this spring has its opposite end retained in a cup-shaped member I48 which seats in the cross web 46 as hereinafter described. The purpose of this spring is such that when the ram piston 86 is projected from the ram cylinder against the roller I I6 it will compress the spring I46 against its seat 46 during the load lifting operation. Upon release of the ram piston the spring will force the outer end of the ram piston back into the cylinder and permit the loadcarrying member to lower.

By loosening the four screws 88 the entire unit shown at the lower portion of Figure 2 may be removed from its seats 50 and 52 formed in the hollow inner walls of the chassis. This unit comprises the head 82 and the connected ram cylinder 84 carrying the ram 86. The plate 15 of the unit forms a shoulder I50, see Figure 7, against which a sleeve I52 is clamped. The opposite end of this Sleeve a ps against a shoulder I54 "formed on a head or casting I56. In addition, this casting I56 is provided with a threaded surface I58 and a relatively small chamber I69 extending beyond the surface I58, which chamber I66 connects by means of a passageway I52 with a reservoir I65 which is formed by a second sleeve "566 which threads into the threaded bore I 58 of the end section I56 and into similar threads I68 of an extension llil on the head plate 15. Thus the 'two sleeves E52 and we are maintained in spaced apart relation to form the oil or liquid receiving reservoir. The end section or casting $56 is provided with a hollow bore I12 which registers with a central conical cavity M formed in the end of the plate '75 and centrally of the annular well .i it. The ram I16 is disposed in this elongated bore centrally of the longitudinal axis cf the two sleeves I52 and IE6. The ram H5 is of smaller diameter than the sleeve H56 so as to leave the annular space H8 therebetween. This space communicates with the small chamber Ii'it. One end of the ram I76 is provided with the usual flexible gasket i8fi held in place by the nut 82. This ram H5 is provided with an elongated central bore 585. into the outer end of which is threaded as at 585 the circular head II 9 that contacts the roller I ll of theload-lifting member, see Figure 4. The threaded bore I95 of this ram H6 is provided with a threaded screw I2 which has an end slot for turning it, and confined and adjusted by this plug I92 is a coil spring lea which presses against a plunger $56 of a diameter smaller than the bore 53a in the ram and at the other end of this plunger 19$ presses against a ball valve 2% which controls a passage 2% formed in the threaded extension 252 of the ram i I5. It is this extension 2i2 that receives the nut 82 holding the flexible washer and packing in place. The ram I26 is provided with a trans verse passageway 254 which connects with the space 296 formed between the plunger Hi6 and the inner wall of thebore 234 of the ram, and this transverse passage 234 in turn connects with the space H8 between the inner sleeve I36 and the ram, which passage in turn connects by means of the chamber its and the passageway I82 with the reservoir.

The spring I54- may be adjusted by means of the threaded plug I92 to any desired tension to control the pressure at which the ball valve I53 is held against its seat, and this in turn controls the pressure in the ram cylinder well Or chamber Il l, as hereinafter explained,

The outer angular surface of the casting I55 seats in the circular bore of the web 56, as shown inFigure 7. .In addition the sleeve .8 when assembled to the section I55, and the plate I5 fit within the circular bore formed in the web 52. The plate I5 is bolted by means of the bolts 88, as here'inbefore described, to the main chassis 2. Thehead 82 is hollow and is provided'with internal walls 2638 which are provided with a bore 2 It the central axis of which lies at an angle of about thirty .degrees with the central longitudinal axis of the ram cylinder and ram, and is also provided with a bore 2E2 the internal walls of which are threaded to receive the threaded end of a relief valve actuator 2 Hi. The longitudinal axis of the bore 2 I2 is likewise disposed at thirty degrees and is parallel to the central axis of the ram cylinder and is, in fact, almost parallel with the longitudinal axis of the bore 2!!! for the high pressure pump cylinder piston. In the bore 2H) is a high pressure pump cylinder 216 herein shown as an elongated sleeve, the outer ends of which are 6 provided with the spaced threaded portions 2I8 and 220, and making a tight fit with the inner end of this sleeve 2I6 is a ball valve cage 222 which is smaller in diameter than the inner wall of the bore 2 I9, and formed integral with or making a snug, tight fit with the ball valve cage 222 is a conical head 224 formed with a liquid passageway 226. The ball valve cage is provided with suitable passages 228, 230 and 232, and the ball valves 234 and 23 which control the ingress and egress of the liquid to the high pressure pump cylinder 2H5. A high pressure pump piston 233 is reciprocable in this cylinder. The cylinder is held in its bore in the unit 82 by means of the annular screw 238 and the packing 2M, and the outer end of the sleeve H8 is sealed by the threaded cap 242 which is apertured to receive the "piston 235 therethrou'gh. The piston 235 is provided with the usual flexible washer and the outer end of the piston .is provided with a yoke 245 which is connected to the piston by means of the threaded connection 258, the furcations of the yoke 246 engaging pin 25%) carried 'by the sector-shaped plates 252 and 25 hereinafter described.

The central liquid passage 22B of the high pressure pump cylinder connects with another passage 253 formed in the unit or casting 208, which in turn connects with the transversely disposed passage 258 which branches and connects as at 266 with the central chamber H t of the ram cylinder "and with another passage 262, the exit of which is controlled by a ball valve 2%. The seat of this ball valve on its seat is in turn controlled by a projection 265 on the end of the elongated valve rod 2 I4. An elongated passage 268 empties into the reservoir at one end and connects with the passage 252 controlled by the ball valve 264. In turn there is another passage 2%, shown in dotted lines, which connects the reservoir with a space 278 formed between the conical nose 224 of the high pressure pump cylinder and the conical walls of thebottom of the bore 2 ID. The pressure relief operating rod 2M passes through a threaded annular cap 28!! that seals packing 282 against its confronting walls to prevent the escape of the liquid at this point. The outer end of the valve actuator rod 2 M has pinned thereto as at 234 a cap 285 which is provided with one part 288 of a universal joint which pivotally connects to another portion 29!! of a universal joint in turn connected to a connecting rod 292 which has furcations 294 engaging a pin 295 therebetween. This pin is formed on the inner side of a sleeve 293 having a flange 3G0 forming an annular keyway 332. This sleeve 298 makes a tight fit in an elongated hollow handle Silt which turnably lies within a. socket 306 of an oscillatable head 388. This socket carries two elongated ears or bearing members are which pivot about the two spaced pins 3 H, see Figure 6, which pins have pivotal bearings in registering openings 3I5 formed in a pair of tongues 3! carried by and formed on the unit 82, which is that part of the unit or head immediately surrounding the relief valve rod 254. By reference to Figure 6 it will be seen that the pins 3 I2 are rotated on their outer ends into the legs am of the actuator handle socket 396 and then inwardly of the threaded part are provided with a further bearing part which passes through the apertures of the two furcated supports 3M and inwardly of this'bear- .ing part the pins 312 areprovided with .a reduced of the sector 252 whereby they may he oscillated. Intermediate of the two sectors is a space through which the interconnected joints of the universal lie. In this manner a construction is provided whereby the universal is interconnected for universal movement about the central axis of the pins 3I2 about which the actuator handle 338 oscillates so that the relief valve actuating stem 2I4 may be mounted centrally of the head 82 whereby only a single universal need be provided between the relief valve and the oscillatable handle that operates the high pressure pump piston while at the same time permitting the relief valve to be turned in any postion of the actuating handle. The sector 252 is provided with registering apertures 3 I 6 which in turn pivot likewise on the pins 3I2. These two sectors are provided with the rigidifying pin 3 I 3 which interconnects them. These sectors are provided with the two parallel stops 320 and are likewise provided with the registering notches 322 and the spaced registering notches 324. The stops are adapted to contact a wall portion 326 of the head 82 to prevent further movement in that direction and the notches 322 and 324 are adapted to be engaged by the latching shoe 328 which has a threaded hole 330 into which a pin 332 is threaded and carrying a head 334. This pin 332 passes through a bore 338 in the handle socket member 306. A coil spring 340 normally projects the latch 328 into engagement with whichever one of the notches 322 and 324 it is desired to be engaged with.

Means is provided for holding the sleeve 298 and the handle 304 in position within the socket 306 and this comprises a pin 342 having the head 344 and a spring 343 which normally maintains the head within the socket 302 while permitting the sleeve 298 to be turned by turning the handle 304. However, when desired, by pulling outwardly on the head 344 the pin 343 is moved outwardly whereupon the handle 304 and the tight fitting sleeve 298 may be withdrawn from the handle socket, the pin 296 of the handle 298 freely coming out from between the furcations in the furcated end of the rod 292. when thus removed the rod 292 is inaccessible for turning. However when the handle and its sleeve with the cross pin 296 are reinserted in the handle so that the cross pin 295 engages between the furcations of the rod 292, then by turning the handle 301 the rod 292 may likewise be turned, which through the universal connection turns the valve operating release rod M4 to unscrew it from its seat and thereby permit the ball 254 to be removed from its seat by the pressure in the ram cylinder whereupon liquid will flow from I the ram cylinder well through the passage 266, thence through the passage 252, past the ball 264, through the passage 268, into the reservoir and the load member will thereupon lower. On the other hand, when the valve rod 2I4 forces the ball to its seat and through the oscillation of the handle member and the sector 252 the high pressure pump piston 233 is operated, liquid will be drawn from the reservoir through the passage 216, into the space 218, see Figure 11, between the conical nose on the pump cylinder and the inner bore, thence through passage 348, past the ball 234, to cause the liquid to enter the pump cylinder. Then upon downward movement of the pump piston 233 the ball 234 will be forced against its seat, to close the passage 348, and the liquid will pass through the passage 228 to release the ball valve 236 from its seat, which will allow the liquid to pass through the cross passage 232, thence down the central passage 226 into the passage 256, through the cross passage 258, into the ram cylinder, to move the ram outwardly of the ram cylinder.

When the ram cylinder is thus moved outwardly, and if the pressure should get too high, that is, greater than the tension of the spring I94, then the plunger I96 is moved to the left to allow the ball valve I98 to move from its seat so that liquid will then be forced through the passage 200 past the ball valve I98, and through the passage 204, thence into the passage between the ram and ram cylinder which connects to the annular passage I60 having at its lower end the passageway I62, back through which the liquid will pass into the reservoir.

In certain instances it is desirable to raise the work holder I22 quickly up to the load, and thereafter to raise the load relatively more slowly. In order to accomplish this there is provided the double acting high pressure cylinder and piston and valve construction shown in Figures 10 to 13, which replaces the cylinder and piston construction shown in Figure '1, all of the other parts of Figure 7 remaining the same. In explaining this construction, by reference to Figure 10, the casting 208 is provided with the same bore 2I0 which at its inner end is formed with inwardly extending conical walls 2I I, which communicate by means of the passage 256 with the cross passage 258 shown in Figure '7. In addition, the conical walls have another passageway 216 therein which is shown in dotted lines in Figure 7 as communicating with the reservoir for the ram cylinder. The conical walls 2| I at their juncture with the passageway 256 make a tight fit, as shown at 251, so that liquid cannot pass from the space 218 to the conduit 250 except that it pass by way of the ball valve cage 350. As shown in Figure 10, this ball valve cage 350 of this construction differs from the ball valve cage shown in Figure '7. The head casting 208 is threaded at its outer end as shown at 352 and into this threads an inwardly finished steel tubing 354. The outer end of this steel tubing is provided with an annular outwardly flared portion 358 to receive a ring-like packing retainer 358 to hold in place the packing 360. This packing tightly engages a piston 362, one end of which is provided with the furcated portion 364 to engage the pin 250 of the oscillatable sector 252 shown in Figures 7 and 8. This piston 362 is provided with a centrally disposed hollow bore 366 which extends longitudinally axially of the piston. Within this bore 366 is located a high pressure piston 368. The piston 362 acts at a lower pressure than does the piston 338. The higher pressure piston 368 is provided centrally axially and longitudinally of the piston with an elongated bore 316 which terminates at its upper end in a narrower bore 312 which communicates with the high pressure cylinder chamber 314 formed in the larger piston 332. A flexible packing 316 is mounted on the upper end of the piston 366 and is held in place by a retaining collar 318 held in position by a nut 380 which threadedly engages a reduced portion 382 formed on the upper end of the high pressure piston. The elongated high pressure piston 368 has on its opposite end a threaded portion 384 which threads into a threaded bore 386 of the valve cage 350. The liquid passageway 310 in the piston 358 extends clear through the projection 388 of the piston 388 which projection is threaded into the bore 386 and the end of this bore 310 discharges .intoa chamber 399 which by, means, of a pas- ;sage 392, opens onto the lower .end of the valve cage or block 355 at the point 3%.

Theterminal opening of this central passageway 392 is formed as anenlarged chamber 393 controlled f ,bythe ball valve 398. In,addition. tothe foregoing, the ball valve, cage 35B hasa terminal passage sac controlled by the ballvalve 432 which closes on a seatdifilcontrolling a passage $93 which hasa right angled passage 493. terminat- 368 whichiis threaded as at 3843 to ,thelcage or block. In addition there is a conical metal end piece illwhich is press fitted as at M4 to an innerlcountersunk portion 455 of this valve, cage 353, and the outerconical end 25? of this piece H2 makesa permanent fit or. tight seat on the wall or seat 21! of the bore 2H3. As stated, he-

foregthe outer annular wall ofrithe valve cage 358 visspaced from theinner wall of the bore 2m to providea, liquid passageway which con nects with thespace Bit and also with the countersunk portion Add. The valve cagedfih is provided intermediate, its ,top and bottomwith a pairof cross bores at right angles to each other.

These intersecting cross bores are 453 and Mil, see Figure 13, and they are preferably. atright angles to the longitudinal axis of the central bore 392 and also to the longitudinal axis of thebore 344. The borer lfiil'has a reduced, portion 422 which terminatesas at 424 in the annular recess did. The opposite end of this bore 426 is closed by a, threaded plug 526. This plug 426 has an extension 428 aroundwhich a coil spring is retained, the outer end of which springlbears against a ball valve 332 which seatsupon the valve seat 43%, see Figure 13, controllingthe bore or conduit 222. The other conduit H8 which is arrangedat right angles thereto and intersects the bore art, has one end closed by a threaded plug see and provides a valve seat 33 normally closed by a ball sec. The valve seat connects with a smaller port 442, see Figure 12, which opens into an elongated vertical bore 4M. extending from the top face 565 of the valve cage which is iii-communication with the space made by the lower end of the outer pressure piston 352 when the latter is moved upward in its cylinder. The lower portion of this vertical passage dad terminates in a valve seat M3 controlled by the ball valve 45%. There is a spring 3-52 confined between the top of the conical end M2 and the valve seat 548 for holding the ball 452 to its seat normally. The bore in which the ball valve can seats is connected by means of a short lateral passage @5 3, see Figure 12, with the annular recessed space ilo surrounding the sidewalls of the ball valve cage.

In the operation of this device, when the larger piston 362 is drawn upwardly, the ball valve 482 Will be raised from its seat so that liquid is drawn from the reservoir I52 through the passageway 276 to the chamber 2l8, see Figure 10, thence by way of .the recessed portion dill to the passageway 408, to the passageway 403, past the raised ball 482, into the larger cylinder, caused by the raising ofthe largerpiston 352. So also on the rise of the piston 3S2, liquid will be drawn from the reservoir through passage 213, space 218, theannular recess M0, through the passage the down stroke of the piston 3$2the ball valve dfiZ closes and the ball valve 432 closes. Liquid will thereupon be forced by the lower end of the piston down through the passage d i hsee Figures l1 and 12, through the passage M2 past the vball i iii which is pushed from its seat, .and thence down the central passage 392,, past ball 398 which is pushed from itsseat, thence through a. passage H3 which is disposed centrally ofthe conical end piece s12, thence through passage 256, thence through passage 258, .see Figure 7,

into the main ram cylinder l'l lwhich will .tend

to urge the ram to the left, see Figure 7., Simultaneously, the liquid that was, confined inwthe high pressure cylinder space 3l' 4, see Figure 10, is likewise forced through .the passage 312, through 1 longitudinal passage 3W3, straight through the, central passageBi-iZ, .past-theball valve 398, through passages H3 and 256,,,to p assage. ,258, into the ram cylinder chamber 114, so thatrthere is produced a pressurerin .therram cylinder equal to the combined volume .of the liquid that is forced both by the pis ton- 362 and also by the piston 3 28. This willraisethe lifting head I22 much more quicklythanrthe, single v piston 233 of Figure 7. Thisaction will take .the lifting head l22up to the load. At this timerthe back pressure due to the, load will increaseaand cause the fluid in the larger outer pump352 to b-y-pass through the ball valve 355) which will open against the tension of the gspringfililt which has a predetermined built-in pressure, and release the fiuid from pump 362thrOl1 h the passageway 45 and into the annular space'llli! and thence into passageway Zld back into the reservoir. Simultaneously with this release of gthe liquid from the larger piston back into the reservoir, but due to the movement of this largerouter piston, the smaller high pressure piston-338 is forcing the fluid in the cylinder chamber 314 to pass through the passages 372 and 310, chamber 398 and passage 392, the valves Mil and 432 maintained closed upon the seats 53-8 and 434, and forcing: the liquid directly through the passage 392, past the ba1l'338, into the passage M3; 256, 258, into the ram cylinder chamber I74 to continue the slower movement of this ram to the left, whereby now more slowly to raise the load-carrying member 122. Thus by reciprocation of the pump piston; the load-carrying member I22 will befirst quickly raised to the load whereupon'the additional back pressure of the load will relieve the liquid that comes from the larger-piston and cause it automatically to flow back into the reservoir, whereas the liquid which is under the iniluence of the smaller piston 368 continues to be forced through the passages as hereinbefore mentioned, into the ram cylinder, to causethe slower movement of the ram to lift the'load. Thus the eifect of the larger piston is automatically cut out during reciprocation of the piston operating mechanism and thesmaller higher pressure pump piston is continued. In shortpin the first part of the operation both pistons operate simultaneously to'produce a quick aproach of the load-lifting member to the load, utilizing speed instead of force, whereas in thesec- 0nd part of the operation the largertppistoneis automatically cut out and thesmaller DiStOl'l-JG- mains operative to lift the .load. Furthermore,

when the load becomes too excessive for the pump, the pressure built up in the ram cylinder chamber I14 will open the valve I98 against the adjusted tension of the spring [94 to pass the liquid through the passages 264, I18 and IE2 into the reservoir.

From the foregoing it will be appreciated that the entire valve mechanism is housed and retained in the valve cage which is located between the pump cylinder and the bottom of the pump cylinder bore, thereby eliminating the necessity of extra valves and valve seats in the base. The entire valve mechanism may be easily removed by unthreading the pump cylinder from its bore.

The spring 433 which closes the ball valve 432 also acts as means to retain the ball 438 against its seat 439 while at the same time permitting it to become unseated.

Obviously the invention is not limited to the specific details of construction disclosed herein but is capable of other modifications and changes which do not depart from the spirit and scope of the appended claims.

Having thus described my invention, what I claim as new and desire to secure by Letters Patent is:

1. A floor jack of the type comprising an elongated. relatively low chassis adapted to be disposed horizontally on the ground, one end of said chassis providing a hollow housing having a circular opening at one end, in combination therewith an hydraulic unit comprising a head having means for connection to the end of the chassis adjacent the opening thereof, said head including a portion provided with a pair of bores, one substantially centrally of the head for a release valve and the other for a high pressure pump cylinder, a piston reciprocable in said cylinder, a valve cage disposed in said pump cylinder and including oil passages therein, said head portion including additional passages communicating with the high pressure pump cylinder and the release valve, a pair of spaced sleeves mounted on said head portion providing a ram cylinder and a liquid reservoir communicating with said passages in said portion, said head portion providing a ram cylinder chamber communicating with said ram cylinder a ram mounted in said ram cylinder and spaced in part from the walls of said ram cylinder. a second head interconnecting the two spaced sleeves, said second head being provided with a central perforation through which the ram is adapted to reciprocate and through which said ram fits in a snug manner, packing means associated with said second head, said packing means contacting the outer'annular walls of said ram, means providing a chamber in said second head communicating with the space between the inner wall of said ram cylinder and said ram, means providing a passage connecting said chamber with the reservoir, said ram having a hollow bore, the walls of said bore of the ram providing a valve seat and a central passage connecting said valve seat with the ram cylinder chamber centrally of said ram, an elongated plunger mounted in the bore of the ram, there being a space between said plunger and the inner wall of the bore of the ram, said ram having a lateral passage disposed adjacent that end of the ram which has the valve seat, a valve normally disposed on said seat, said valve being normally contacted by said ram plunger, a coil spring in the opposite end of the bore of the ram and contacting the outer end of said 12 plunger, and an adjustable threaded plug mounted in said bore to adjust the tension of said spring, and a head threadedly mounted on said ram.

2. An hydraulic jack comprising a base having apertures therein and a ram cylinder chamber, a pair of sleeves mounted on said base in spaced relation to provide a reservoir, the inner sleeve providing a ram cylinder, a ram reciprocably mounted in said inner sleeve and spaced throughout a portion of its length from the walls thereof to provide a liquid passage, a head spaced from the base and interconnecting said sleeves at their outer end, said head being bored, a ram snugly reciprocable through the bore of said head, packing means in said head adapted to engage the annular walls of said ram, said ram having a central bore therethrough, the inner end of said bore providing a valve seat and a centrally disposed passage connecting with the ram cylinder chamber, said ram having a lateral passage connecting the bore of the ram with the space between the outer wall of the ram and the ram cylinder, said head having a passage formed therein connecting with the space between the inner wall of the ram cylinder and the outer wall of the ram, means formed in said head connecting said passage with the reservoir, an elongated plunger mounted in the bore of said ram, a ball valve disposed between the plunger and said valve seat, the outer portion of the inner bore of said ram being threaded, an adjustable plug engaging the threads of said bore, a coil spring disposed between said plug and the outer end of said plunger for resiliently engaging the ball on its valve seat, a high pressure pump mounted in a bore in said base, a release valve mounted in another bore of said base, said base including valve controlled passages interconnecting the ram cylinder chamber and the reservoir and the high pressure pump, and means for reciprocating the piston of said high pressure pump and for operating said release valve.

3. A cylindrical block-like hydraulic pumping mechanism of a jack comprising an elongated cylindrical block having opposed faces, the annular cylindrical wall between said faces being provided with an annular countersunk portion to provide a liquid passage, said block along its central axis parallel with said countersunk portion being provided with a central passage extending from face to face of said block, the end of said passage at one of said faces of said block being provided with a valve seat, said block at the opposite face being provided with an opening disposed laterally of said central passage and provided with a valve seat and a connected passage extending part way through said block in a direction substantially parallel with the central passage thereof, said connected passage having a lateral extension connecting with the annular countersunk portion of the block, said block having a third passage spaced from the central passage and extending substantially parallel to the central passage of the block, said third mentioned passage extending from said second face of the block to a point adjacent the opposite face, at which point said third mentioned passage is provided with a valve seat and a lateral passage connecting with the annular countersunk portion of the block, said block also having a pair of passages transversely disposed with respect to each other and extending completely through the block in a direction at right angles to the central passage through the block, said angularly disposed passages interconnecting with the central passage, one of said pair of angularly disposed passages being provided with a valve seat and interconnecting with said third mentioned passage, said passage at its other end having a plug to obstruct connection with the annular coun" tersunk portion, the other mentioned passage of said pair of passages having a connection with said countersunk portion and having an associated valve seat and valve, and the opposite end of said last mentioned passage being blocked from communication with said annular countersunk portion.

4. In a floor jack of the type having a chassis adapted for disposition horizontally on the ground and which chassis has a load lifting member shiftably mounted thereon for elevation to raise a load and which also has an hydraulic unit mounted thereon, said unit including an actuatable ram positioned when the unit is so mounted to actuate the load lifting member, and wherein said unit further includes hydraulic pumping means having a piston and a release valve disposed substantially centrally of the unit, there being means for mounting said unit on said chassis, and said unit carrying thereon a pair of spaced, elongated supports having bearings on their outer ends, in combination therewith a turnable handle socket for actuating said pump piston and for actuating said release valve, said handle socket having furcations provided with registering apertures, a pair of spaced pins passing through the apertures of said furcations and engaging the apertures in said spaced bearings, an oscillatable sector having spaced openings, said pins having bearing members on their inner ends adapted to enter the bearing members of said spaced sector, said spaced sector being rigidly interconnected but being disposed between said elongated bearing members of said head, spaced notches on said sector and a shiftable latch mechanism carried by said handle socket and adapted yieldingly to engage in a desired notch of said sector to interconnect the handle socket and sector for oscillation together, an elongated tubular handle, a sleeve carried by an end of the tubular handle, said end being insertable in said handle socket, said sleeve having a connector therein, an elongated turnable actuator mounted in said handle socket and projecting into the socket aperture detachably to be engaged by the connection of said socket sleeve whereby said connector may be turned by turning said handle, and a universal connection on the other end of said elongated connector and connected to said relief valve, said universal being disposed between said elongated bearing members of said base, and shiftable latching means carried by said handle socket for allowing said handle to be withdrawn from said handle socket, or alternatively for locking said handle to said handle socket while at the same time permitting said handle to turn relatively to its socket to turn the valve.

JOSEPH J. MUELLER.

REFERENCES CITED The following references are of record in the file of this patent:

UNITED STATES PATENTS Number Name Date 306,060 Cook Oct. 7, 1884 468,104 Weeks Feb. 2, 1892 1,610,499 Dybens Dec. 14, 1926 1,715,901 countryman June 4, 1929 1,745,024 Malone Jan. 28, 1930 1,812,577 Albertine June 30, 1931 1,834,547 Nilson Dec. 1, 1931 1,907,085 Nason May 2, 1933 2,038,974 Werner Apr. 28, 1936 2,042,186 Peterson May 26, 1936 2,044,857 Pfauser June 23, 1936 2,145,014 Rosenberry Jan. 24, 1939 2,146,403 Nilson Feb. 7, 1939 2,156,543 Pfauser May 2, 1939 2,284,615 Kligman May 26, 1942 2,370,681 Mueller Mar. 6, 1945 FOREIGN PATENTS Number Country Date 765,560 France of 1934 768,298 France of 1934

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