US1308844A - And william e - Google Patents

Description

W. FERRIS AND W. E. MAGIE. HYDRAULIC TRANSMISSION DEvIcE.

APPLICATION FILED FEB. 26.l i916.

W. FERRIS AND W.; E. MAGIE.

HYDRAULIC TRANSMISSION DEVICE.

` APPLICATION man FEB. 2s. 1915.

Patented J illy 8, 1919.

w. mams AND w. E. MAGIE.

HYDRAULIC TRANSMISSION DEVICE.

APPLICATION msu FEB. 2s, Isls.

1,308,844. I A I PatentedJu1y8,1919.

4 SHEETSSHEET 3.

I I I I l w. Finals AND w. "E. MAGIE. HYDRAULIC TRANSMISSION DEVICE.

APPLICATION FILED FEB. 26. |916.

D? m m 8 SMU 0, 1. MVM

STATES PATENT oFFIoE.

FEBBIS, E MILWAUKEE-WISCONSIN, AND WILLIAM E. MAGIE, 0F n EVANSVILLE, INDIANA. 'I

I HYDBAUIIZIC TRANSMISSION DEVICE.

Specification of Lettersv Patent.

' Applicatioii led February 26, 1916. `Serial No. 80,580.

To all whom t may'concer'n.' a

Be it known that we, WALTER FERRIS and i lWILLIAM E. MAGIE, citizens of the United States, residing, respectively, at Milwaukee, Wisconsin, and Evansville, Indiana, have 1nvented certain new and useful Improveing, to 'improvements in ments in Hydraulic Transmission Devices,

a specification. generally speakydrauhc transaxial type wherein Our invention. relates,

missions of the so-called the motor and pump cylinders and istons p are all arranged ingroups axially a out a reservoir or make-up chamber.

central shaft.

In our preferred and pump together with the operating mechanism are all `contained wlthin a single housing. This housing `forms what we prefer to call an operating chamber. Within it is: a pressure chamber comprising the the oil orliquid under pressure within the pump and motor cylinders, valve plates, ports and passages. A portion of the housing isgiven over to a This chamlrber is adapted to contain a certain amount of Vmotive fluid in a condition of rest and means are provided for forcing this iiuid from the make-up chamber back into the' operating chamber either by the pump or hydrostatic pressure or otherwise. A pres sure' reliefl is provided for the operating chamber and the operating chamber is 1ntended to be at all times completely filled with the motive fluid at acertain predetermined pressure." Any introduction of more fluid-will only result in'increased pressure and a. controlled discharge from the operatl 4 ing chamber to the reservoir. Since the opmotive fluid, oil leakage from the main pump erating chamber is allthe time full of the into'4 the operating chamber immedlately l 410a-mnd' this supply wiu ke@ 5o forces an equal exhaust port, `illn eating therewith.'

quantity of oil back into the the cylinders communin our preferred-form we `provide a circulating pump which will con-- stantly force a small supply of motive fluid from the reservoir into the worklng chamup therpressure to the desired point and eep the .working chamber -always filled. To permit this pump always to' operate there must be a relief-valve and this relief valve-is set to keep Aa certain predetermined pressure in the. valve chamber. j

form-of device the motor Patented July s, 1919.

Our invention is illustrated more or less diagrammatically in the' accompanying drawings, wherein Figure 1 is a longitudinal section through the housing and parts contained therein with parts omitted;

Fig. 2 is a detail section on an enlarged scale showing part of the driving and swash plate connections; y

Fig. 3 is a 'section on the line 3 3 of Fig. 2;

4 is a section on thel line 4-4 of Fig. 2; Fig. 5 is an enlarged detailed the circulating pump;

Fig. 6 is a section on the line 6-6 of section of Fi 1' l Fig.7 is a part elevation and part section along a plane perpendicular to the'plane of the section of 'Fig. 1; and

Fig. 8 is a section of the cylinder ports where they engage the valve plate.

Like parts are indicated 'by like letters throughout the several figures'.

Housing.

The cylinder `housing in which'y all the working parts are contained is made' up 'the v-alve housing but closed at the other end except for central axial apertures A8, A. Curved annular walls A, Apinthe ends of the housings A1, A2 -form reservoirs or `ma'ke'up chambers A", A8. These reservoirs or make-up' chambers may be regarded as one because they are connected by a pipe A", a portion'of which is coiled as at A to provide a cooling or radiating surface whereby the temperature of the oil .may

dangerpoint. A

In the wall of the housing A1 is a screw threaded adjustable plug B. This plug is in line with an aperture B1 in the wall A? and slidably mounted within this aperture is a. pressure relief valve B2. This pressure relief valve is adapted to be yieldingly seated against the wallv A5 by the spring B3, the

v100 be kept down below a certain predetermined up4 of a plug 1n which are cut a series of* slots B4 increasing in Width inwardly so that as the pressure in the main Working chamber increases pressing back the4 valve against thespring any fluid in the housing Will be free to pass out through these slots.

, The greater the pressure and the further l the aperture ably connected for driving with any desired theC plug is moved the greater the eii'ective opening through which such fluid or liquid may pass.

Formed 1n the vvall A6 is a circulating pump housing C. This pump is a single acting pump havin a piston C1 drivenl by a connecting rod 2 reciprocating in a -cylinder C5 located in the housing C. C4 is a spring seated intake valve, C a springy seated exhaust valve so that as the pump reciprocatesthe oil is drawn from the reser- Voir As through the intakev valve C4 into the cylinder C5 and thence expelled through the exhaust valve C5 to the interior ofthe Working housing. i

The housings A1., A2 are lbolted to the housing A by means of the cap screws A11 as indicated. The flanges between these two housings are protected againstJ leakage by the annular rings A12 yand bleeder tubes leading therefrom through pipes A12 communie-ating With the ipe A5, thus relieving the outer portion of t e packing surface between'these flanges from the direct pressure of the -oil in the Working chamber.

y Operating' skafts ami supports. D is a pump shaft projecting out through 4 in the housing A2 vand suitprime mover not here shown. D1 is a packving; D2 al, packing ring and D5 a holding- (Tap-l 'the4motor out through the' aperture A5 and D4 1s a motor shaft leading from adapted to deliver its power in .any suitable manner. It also is packedas indicated at theother end of the machine. The shafts D and D4 are each guided and supported adjacent the ends of the housing by the floating bearings D5. These bearings have spherical ends D6 engaging the spherical surface D7 on the housing so that they will be free to move 4and adjust themselves for any bending or change in position of the shafts and prevent distortion of the partsl and any binding -or frictional losses. D8 is a centrally disposed hub furnishing separate bearing `surfaces Afor each of the shafts D, D4. Contained Within the center of this hubis a plug E. This plug E is longitudinally apertured and has at either end the pipes E1,

E2 projecting into the ends of the shafts D D4 respectively. These shafts contain oil passages Es leading longitudinally from the ends of thev pipes E1, E2 to transverse pipes E4. These transverse pipes E4 com- Within Vthe blocks D5 behind the slidable collar or plunger E5. The slidable collar E5 is in engagement with a shoulder E7 011 the.

shaft so that any oil forced in through the kbearing block in the other direction toward the spherical bearing surface. lAn eccentric lpipes E3 and E4 to the annular chamberl E5 is provided on the shaft D to drive by.

means of an eccentric collar E9 the connectf ing rod C2 to operate the circulatlng pump.

The bearing on the shaft in the bearing block is lubricated by the QH flow from this same tube and annular chamberl and a bleeder .pipe E1o leads from the bearing to perm-it run-off of excess oil and to prevent the full oil pressure from coming upon the acking sleeve at the end of the shaft. f here is also a bleeder pipe E11 as indicated to permit out flow of oil from the space betv veen the bearingblock and the housing to the reservoir.

Valve plate and cylinder bmw-el assembly.

F is a valve disk or plate. It 'is as shown centrally located in and integral with the member A and carries the hu-b D5. This valve plate has through it tWo (crescent shaped ports F1, F2. These ports may each of `them be either an intake or an exhaust port depending on the direction in which the machine is running. When one is an intake' the other is always an exhaust port. F5, F4 are relief passages leading from the ports F1, F2 respectively. 'These passages are controlled each by a safety valve F5 pressed upon a seatF6 by the spring F7 the tension in which may be adjusted'by manipulation of the screw-threaded cap F5. When the pressure is suliiciently great to raise this valve the liquid escapes into the valve chamber F" thence through the bleeder pipes F15 to the interior of the housing.' F11, F12 are housing so that 4-vvhen the pressure in one por-brises above the safety point and the relief valve is unseated the oil thus forced into `the housing willraisethe pressure there and cause oil'to be forced from the housing through the return valve into thel opposed' `port, thuskeeping the pressure chamber al- Wa s completely filled.

is a pump barrel, G1 a vmotor barrel. Y

These barrels are, generally speaking, similar one to the other. They are mounted for krotation each u on one-arm of the hub D13A and gu-idedan supported thereon. Each inder.

' than they are in' a radial direction because this best utilizes the available space and because the area of contact between the barrel and valve plate is thus reduced to a minimum: They discharge each against the valve plate F and are of substantially the same width measured along a radial line as the ports F1, F2. These ports are controlled by, and' discharged through, the valve plate F. In each cyllnder is a iston Gr free to move back and forth therein. These pistons contain each a spherical bearing G in which sets a ball G8 on the end of a' connecting rod G2. The ball Ais held against the bearing by a disk G1 having a spherical, bearing thereupon. This disk is held in position by a follower nut G11 so as to hold the connecting rod firmly in position in proper relation tothe piston. The center of the piston is apertured as at G12 in registerJ with an oil duct G13 through the connecting rod. G14 is a coil spring anchored at one end in the piston G and at the other end in the follower'nut'Gr11 so that as wear takes place on the sp'herical bearing the spring tends to rotate the follower; nut to ti hten 1t on the ball.

4neled driving block ring H H is an annular ring ormed on the wall i 35 "A inclined tothe axis of rotation of the shaft, its center being so located as to bring Y its axis to an intersection with the shaft axis inthe plane of the connecting rod sockets.

On it rests a flanged guide sleeve H1, the.y

flange H2 thereof containing the ball race H15 H1 areballs travelin alon the ball race and supporting a mova le ba l race H5. This ball race I-Ii carriesvan annular chanided on sleeve H1 and contalmng spaced t ereabout seven These drivin blocks s to en- H" on the ends of the connecting rods G. These balls are held firmly seated on the spherical bearings b the follower rings H1 which are slidab e toward and from the bottom of the block.

lI is an annular spring late having Iseven apertures therethrou h w ich apertures are in'engagement-with t e projecting fianges I1 on the follower rings. This s ring plate holds eachI and every one of the follower 'rings bound in position to clamp. the ball -ends of the connectin rods close 'in their sockets.- This plate is eld in position by a lurality of cap screws I2 which pass through 1t and engage the ring H at p omts removed from the follower rings so t Vring'` is not supported/at those points and thus transmitting yieldin'gly at the spring presses down pipe J 9 this pressure to the follower rings-to hold .them in position and thus by the yielding pressure of this plate each follower ring is caused to automatically follow up and compensate for any wear in the ball end. I3 is a s Ppi-ing ring mounted on each of the sleeves 1 and J and held rigidly thereon by the cap screws I". This spring ring overlies the channel ring .H0 and presses yieldingly against itr and holds that ring yieldingly but 'firmly against the ball bearing. The above description applies to both the um and the motor ends of the apparatus, ut t e pump 'end is exactly the same except that the swash plate assembly consisting of the ball bearing, the annular ring and the 4blocks which drive the`connecting rods, are

mounted forrotation about an axis at right angles to the shaft, so as to permit adjustment of the stroke of the pump. No such adjustment of the motor is usua l needed, andso the motor parts are shown lixed in position.

'In the pump assembly then the bearing sleeve or quill J is substltuted for the bearing sleeve H1. This quill J is mounted on the yoke J2, which yoke is provided with a pin J2 pivoted `in a bearing plug" J 1 at one side of the housing A2, and provlded with a control shaft J plvoted at' a plugJ at the other side of thel ring, and J s a packing sleeve to prevent leakage of the oil along the shaft, the bleeder discharging from a point inside the packing ring into the reservoir A, so that the pressure on the packing sleeve is only the pressure in the reservoir, the bearing J1 being thus lubricated by the roil escaping from the working chamber. The shaft 5 is square as at J 11 so that it maybe manipulated by any suitable wrench, handle .or the like to adjust the inclination of the swash plate and thus the stroke of the pump. J 12 is a filler plug discharging into the reservoir As, whereby the supply of oil may be replenished. It will be noted that the axis of the shaft J '1 and pin J 8 intersects the pump shaft at the same point that the' plane located by the centers ofthe outer end balls lof the connecting rods, when'the swash plate occupies a neutral position, intersect this shaft, so that no matter what the inclination of the yoke, the movement of the swash plate, whose plane is the plane above referred to, is symmetrical with respect tothe .pump shaft.'

The parts housing. J7 is a packing interposed between 4the bearing sleeve J andl the pistons Go are, of course, lexactly the same as the parts interposed bewith the cylinder barrels, and since these barrels are mounted on the shafts as shown, a' connection between the shafts and the swash plates is necessary. In the case of the pump, the angle of the swash plate is variable, and this connection must, therefore, be by means' of some type of universal joint and this universal joint connection takes care of this inclination and permits a continuous drive. It is also important that the angular rotative position of the swash plate with respect to the shafts be fixed or constant, and since the ordinary or universal joint does not get this desired result, it is necessary to employ a special type of universal joint which will drive the driven part so that its angular position will always be the same with respect to the angular position of the driving f Y has on eitherV side midway the trunnion part, 4.that is to say, a universal joint which has what is called a constant velocity ratio.

K is a hub keyed vto the shaft. It carries a spider K1L having a ange K2. On this flange is pivoted a warped ring K3. This ring is trunnioned at c k on two diametrically opposed sides on the flange K2, and

points, a pivoted 'bearing K4,- to which is joined by means ofthe screw K5 a pivoted i bearing K6 on a somewhat similar ring K7.

This ring is slightly smaller in diameter than the ring K3, and is pivoted on opposed sides halfway between the pivoted bearing Kon pins KS, which project from the ring spider4 K1, is located partially within the cylinder barrel. This hub is, of course, keyed to the shaft, and has resting against it an annular washer L surrounding the shaft. This washer has a spherical surface L1 in engagement with a spherical surface L2 on a compensating washer L3, which is supported by the cylinder barrel. Thus the thrust of the shaft operates to hold the cylinder barrel firmly and snugly against the valve plate, independent of. any distortion or displacement of the shafts. The barrels themselves are driven in unison with the driver by pins L1 projectingl therefrom in engagement with the yokes L5 on the driver.

Resum.

The pressure chamber, as above pointed out, comprises the spaces between the pistons and the valve faces on the pressure side in pump cylinders and motor cylinders; the volume of the main ports in the valve plate, the auxiliary ports to the double check valves, the passages E3 inshafts, and the pressure chambers backl of the plungers 'E6 on said shafts. All of the leakage from this pressure system goes either directly into the operating chamber past the pistons and valve faces or is returned thereto after leaking from the pressure chamber, along the ducts `or between the bearings or past the collars or plungers E6, as the case maybe.

The operating chamber or inner casing is the space containing the cylinders, valve plate, universal joints and thrust bearings,y

cludes return ducts which receive the leakage around the shaft from pressure chambers back of plungers E6 and return it to the main operating chamber, thus relieving the circulating ump from the work of returning this leakage from the reservoir system. The piston and cylinders are of` uniform size and stroke, and the ports ofthe valve plate of equal size, and opposite each other. They are so placed as to-insure the division of the'operating chamber into zones of high and low pressure of equal size. This is the case since the valve ports are disposed at equalI distances on either side of a line through the center of the valve plate, and at right angles to the axis of rotation of the piston controlling ring. The reservoir or make-up chamber is in this case dividedv intotwo .sections A7 AB, one at each end of the machme, and connected by an `exterior pipe. The reservoir is characterized by the fact that it is normally partly full of oil,

the remainder being filled with gaseous material, capable of accommodating oil eX- pansion, the pressure being lower than -in the operating chamber. The pressure in the reservoir may be substantially the same as that in the operating chamber if the machine is built without a circulating pump; or the operating chamber pressure maybe considerably higher than the reservoirpressure, this increase'being incidental to the operation of j the circulating pump. The reservoir system also comprises the leakage return ducts near the ends of the main shafts, the end of the operating shaft, from the flanged joints, and the return pipe from the auxiliary or 1 relief valve reservoir to main or pump reservoir. Duets receive the leakage :fromv the leakage is automatically returned from the lowest pressure zone into the next pressure operating chamber system along the main shaft and operating shaft, and return it directly to the main reservoir,thus relieving the shaft packings from the work of holding back the pressure of the operating chamber. The shaft packings are therefore only subjected to reservoir pressure, which `in most t cases will f approximate atmosphere pressure, or may be lower.

From the above it appears that thev entire casing is divided into three zones of pressure. passing automatically into the next lower zone.l vThe packings around the external shaft openings only ha\'e to hold the pressure of the lowestl or reservoir zone. The

zone or operating chamber by the expansive pressure of thet gas or air which occupies part of the reservoir system or by the circu-v lating ump when the circulating pump lis used. his circulating pump will also serve to augment the pressure in the operating.

chamber when so desired. Certain advantages in thefoperation of the machine can be attained by a gradual circulation of the oil from the reservoir into the operating chainber and back again. These advantages lie principally in giving each fraction of the oil in turn an opportunity to leavethe operating chamber, where it is violently agitated, n

and spend some time in the reservoir-,where it is practically at restand has a chance to deposit any solid matter held in suspension,

y and to free itself from `entrained air. This circulation is maintained'by means of the j plunger pumpfof small capacity andin this trans casel operated by the eccentric formed on the main pump shaft. At each stroke this pump voir to operating chamber throu h the check valves and an equal uantity is orced out of y v the operating'cham r through the relief 1valve,- returning to the main reservoir through the connecting pipe. An additional advantage of this circulating. system is-thecooling yeii'ect of the exterior pipe, which, if desired, may be expanded into coils or a radiator A1", thereby radiating any necessary amount of heat from the oil. Certain other advantages may be gained by carrying a com aratively high pressure in the operat- .ing c amber. This merely requires additional spring pressure on the relief valve B. It is also advisable to design the relief valve in this case as a plungerV having Aports of graduated area.l By adjusting the spring the seats is returned to The leakage from each higher zone' ers a small quantity of oil from reserof pump. 'The advantages of this Pressure l system comprise better lubrication due to initial pressure on edges of oil films; reduction in necessary'size of leakage return ducts whereby leakage past main piston and valve ressure chamber; suppression of tendency 1n oil to volatilize under high temperature, thereby preventin formation of gasbubbles. The ports G4, 5 in the ends of cylinders prefera' ly have equal or greater area than the cross section of cyliners themselves. This provides large port area, thereby permitting great speed and.`

great efliciency. In order to compensate for .the enlarged ports which prevent pistons from holding cylinder ba'rrel against valve seat, we introduce shaft and closely lungers integral with tting in the pressure chambers, which are formed in the self-alining shaft bearings. The driving pressure-is automatically maintained in these pressure chambers through ducts in the shafts and the check -valve therein. The shafts are mountedin selffalining end bearings which` permit a close fit between shaft and bearing to prevent excessive oil leakage from the pressure chambers, and at the same time prevent crampin in bearings due to slight shaft deflections.

4 lie drivers lK1 are keyed to the shaftsl behind the end thrust shoulders and the balance pressure from the chambers Es is communicated to the barrels Gr-G1 through pairs of compensating washers L1 L3. This gives perfect valve face bearing independent of4 shaft deflections. The barrels are compelled to rotate with the driver by the drivmg pins L4 which transmit only the torque of valve face friction: The compound universal joint .consists in a driver and a driven ring, eachl carrying a pair of pins on the transverse axes respectively.- On these two pairs of pins are res ectvely mounted two connecting rings. hese connecting rings are pin connected together on a transverse axis which intersects -the axis of the shaft tol .which thedriver is connected and 1s preferj. ably perpendicular to the .planes of the axes of the driving and driven rings when they i occupy neutral positions. The plane vin whichthis transverse axis revolves bisects the angIle between the shaft and swashplate, axes.

f here is a slight axial motion as the joint revolves which in the present 'invention is permitted by a small sliding movement of a sliding block at one trunnion atv the lower side of the ring thus preventing binding or distortion. In order to take up all wear in the driving parts, and to prevent backlash to as great an extent as possible, it is necessary to provide means Afor holding the ball ends ofthe connectin rods firmly back in the pistons or in the rivin blocks on the swaslr plates. The blocks an the `swash plate all rotate, but in the-same plane are held by a `single annular plate I.of springbrass or` spring steel, having seven'equally 'pitched holes which are slipped over projecting flanges on the follower rings which hold the ball ends of the connecting rods close into' the sockets.. This plate is held down by seven screws which are tapped into the socket ring. These screws pass through the spring plate at points between the connecting rods where the plate is unsup orted and the screws spring the plate Isu ciently to cause it to automatically follow up any wear 'in 'the ballvends, or in the sockets. Th'e arings, a spring ring I3 is secured to the bearing quill or sleeve J. The end of this bearing quill is faced off slightly shorter than l the corresponding face on the socket ring, thereby giving the spring ring a deflection which always holds the socket ring tightly back against the ball thrust bearings. These three devices, which together we term a spring harness, absolutely prevent any backlash in the movement of the pistons. With this arrangement there xis no excess pressure in the exhaust port bto keep the pistons forced outward, and the spring harness supplies this need. This .is a distinguishing point between the present system of returning leakage by casing pressure and the system of returning leakage by a pump, which has, been embodied in various other machines.

f Referring again to Fig. c, a 'will be noted Vthat the ports orl terminations of the dis-l charge passages Gr4 leading from the cylinders to the valve plateform segments of a ring bounded by two concentric circles g, g",

each segment being separated from its neigh- -bor on either side-.by a thin partition wall bounded by adjacent radial lines, g2. Each port thus has two straight and two curved sides, the straight sides radiating from the too rapid leakage along the sealing surfaces.

center of the valve plate, and the curved sides formed by concentricv circles drawn about thecenter'of the valve plate. Each port resembles in shape a truncated pie segment.l The opposed surfaces between the outer rim of the valve face and the concentric circle forming the outer side ofthe ports,

constitute an oil seal. The distance betweenv the two surfaces niust'not be any` greater than is absolutely necessary to prevent the The circles bounding ,the outside and the inside of the valve plate port are of equal diameter with those bounding the cylinder ports and are drawn about the saine center. There is anappreciable pressure in the film of oil forced out between these surfaces and this pressure tends to wedge the cylinder barrel away from the plate so that the smaller the surface the smaller the wedging. effect. The substantially radial lines bounding the ends of the ports are about the same distance apart as the concentric lines above mentioned, so that the oil seal at the ends of the ports is substantially the same as at the side. When once the necessary width of surface to provide an adequate oil seal has been determined, and when once the area of the ports and the cylinder passages have been selected, the remainder of the Valve seat mustbe ina-de to conform in such wise that for any given mean radius minimum possible unbalanced wedging area. l

It will be understood that the unbalanced wedging or thrust area forming a part of the oil seal supports a pressure which must be overcome by some suitable externa-l or internal means, as preferably the balancing plunger described at another place.

We claim: Y l

1. A hydraulic transmission comprising a motor and a pump, a pressure chamber contained within and connecting them, a closed housing surrounding them, and means for keeping said closed housing completely full of'oil under pressure.

'2. A hydraulic transmission comprising a motor and a pump, a pressure chamber contained'withinvand connecting them, a closed housingsurrounding them, and means for keeping said closed housing completely full of oil under pressure, a connection between said pressure chamber and said housing, and means responsive to the operation of motor and pump for controlling said connection.

3. A hydraulic transmission comprising a motor and a pump, a circulating system connecting them having a pressure and a suction side, a closed housing surrounding them, and means for keeping the closed housing constantly full of oil under pressure, separate connections between the pressure and suction sides of the circulating system and the housing, and means for controlling them.

4. A hydraulic transmission comprising a motor and a pump, a pressure chamber contained within and connecting them, a closed housing surrounding them, and means for keeping said closed housing completely full of oilfunder pressure, a connection between said pressure chamber and said housing, and means responsive to the operation of motor and pump for controlling saidv connection,

.said means comprising a series of passages, a

,pressure relief valve controlling one of them anda check valve controlling another.

5. A hydraulic transmission comprising a motor and a pump, a circulating' system con- `nectin them having-a pressure and a suction si e, a closed housing surrounding them,

and means for keeping the closed housing constantly full of oil under pressure, separate connections between the pressure and suction sides of ,the circulating system and 'the housing, .and means for controlling them,

said means comprising a series of passages,

- a pressurel relief .valve controlling one of them, and a check valve controlling another. 6. A hydraulic transmission comprising a motor and a pump, a circulating system connecting them having a pressure and a suction side, a closed housing surrounding them, and means for keepin the closed housing constantly fullof oi under pressure, separate connections between the pressure and suction sides of the circulating system and the `housing, and means for controllin them, said means comprising passages lea in from the pressure and suction sides, are ief valve controlling the passage from the pressure side, and a check valve controlling the passage from thesuction side.

A hydraulic transmission comprising a motor and pump, a pressure chamber contained within and connecting them, a closed housing surrounding them, and means for keeping said housing constantly full of oil under pressure, and for circulating said oil through said housing independent of conditions 1n the pressure chamber.

8. A hydraulic transmission comprising a motorl and pump,v a pressure chamber contained'within and connecting them, a closed housing surrounding them, and means for keeping said housing constantly full of oil i t under ressure, and for circulating said oil i throug said housing independent of conditions in. the pressure chamber, said means comprising a reservoir and means for pumping oil from the reservoir into said housing. 9. A hydraulic transmission comprising a motor and pump, a pressure chamber contained within and-connecting them, a closed housing surrounding them, and means for keeping said housing constantly full of oil under ressure, and for circulating said oil `and throug said housing independent ofconditions in the pressure chamber, said means .comprising a reservoir-and means for pumping oil from thelreservoir into said housing, Y ressure relief means discharging 'from said 'ousing to saidreservoir.y

10..In a hydraulic transmission a fixed valve plate, a cylinder barrel4 mounted forl rotation having its discharge end closed by Vsaid late, cylinders contained within said 4barre discharge ports leadingfrom saidlcylinders `to the plate larger in cross sectional area 'than the cylinders, and means removed from the barrel for holding itagainst the late. v

11. In a iiydraulic transmission a valve plate, a cylinder barrel mounted for rotation with respect to said late, discharge ports leading from the cylin ers therein and controlled by the valve plate said cylinder ports being larger .in cross sectionall area than the respective cylinders, means for maintaining a hydraulic pressure within such cylinders and plate, and means responsive to such pressure for holding the cylinders firmly against the plate.

12. In a hydraulic transmission a' valve plate, a cylinder barrel mounted for rotation with respect to said plate, discharge ports 'leadin from the cylinders therein and controlle by the valve'plate said cylinder ports being larger in cross sectional area than the respective cylinders, means for maintaining' a hydraulic pressure within such cylinders and plate, and means responsive to such pressure for holding-the cylinders against the plate, said means comprising a plunger, a connection between the plunger and the barrel., a c` linder in-Which said plunger operates, an ,a connection from the pressure system to said cylinder.

13. A hydraulic transmission comprising a motor and pump, a pressure chamber contained within and connecting them, a closed housing surrounding them, and means for keepingl said housing constantly full of oi-l under ressure, and for circulating said oil throng said housing independent of condi' tions in the pressure chamber, said means comprising a reservoir and means for pumping oil from the 4reservoir'into said housing, l

and pressure relief meansdischarging from said housing to said reservoir, said pressure relief being provided with means responsive towariations in the pressure 'of the oil in the housing for contrlling the amount of oil discharged therethrough.

14. In a hydraulic transmission a fixed valve plate, a cylinder barrel mounted for rotation having its discharge end closed by Ameans for holding the barrel against the plate.

and controlled thereby, a shaft concentric with the barrel and having driving connection therewith, pistons and means for reciprocating them lwithin the cylinder barrel as the shaft and barrel are rotated, and hydraulic means removed from the barrel for yieldingly holding it against the plate, the shaft being perforated and communicating respectively with the ports of the valve plate and with the saidhy-draulic means whereby pressure for operating the latter is taken from the pressure port of the valveplate through the shaft.

18. A hydraulic transmission comprising a valve plate having ports serving alter- `nately as intake and exhaust ports, a cylinder barrel mounted for rotation with respect thereto and having its discharge end closedand controlled thereby, a shaft concentric with the barrel and having driving connection therewith, pistons and means for reciprocating them Within the cylinder barrel as the shaft and barrel are rotated, hydraulic means removed from the barrel for yieldingly holding it against the plate, the shaft being perforated and communicating respectively With theponts of the valve plate and with the said hydraulic means whereby pressure for operating the latter, is taken from the pressure port of the valve plate through the shaft, and valve means for selectively closingithe connection with the exhaust port of the .valve plate and opening that with the pressure port.

` 19. A hydraulic machine comprising a valve plate having annularly arranged intake and exhaust ports, a cylinder barrel mounted for rotation with respect thereto having axially arranged cylinders of greater diameter than the radial width of the ports leading from said cylinders to said ports in the valve plate, said cylinder ports where they discharge 'into the valve plate ports being of substantially the same radial width as such ports and being bounded at their lends by radial lines and at their sides by concentric circles and narrow dividing'walls between said cylinder ports.

' 20. A hydraulic machine comprising a take and `exhaust valve plate having annularly arranged intake and exhaust ports, a cylinder barrel mounted for rotation with respect thereto having axially arranged cylinders of-greaier diameter than the radial width of the valve ,plate ports, cylinder ports, leading from the cylinders to the valve plate, such ports where they discharge into valve plate ports being of substantially the same radial width as sa i such ports and being bounded at their ends by radial lines and at their sides by concentric circles. Y i

21, A hydraulic machine comprising a valve plate having annularlyarranged in-` take and exhaust ports, a cylinder barrel mcanted for rotation with respect thereto having axially arranged cylinders and ports leading from said cylinders to said valve plate ports,.said cylinder portswhere they discharge into the valve plate'ports being of substantially the same radial width as such iponts and being bounded at their ends by radial linesand at their sides by concentric circles and-narrowdividing' walls between said ports.

22. A hydraulic machine comprising aV valve `plate having annularly arranged intake and exhaust ports, a cylinderV barrel mounted for rotation with respect thereto having axially arranged cylinders andports leading from said cylinders to the valve plate ports, said cylinder ports where they,

discharge into the valve plate ports being of substantially the same .radial Width as such ports and being bounded at their ends by radial lines and at their sides by concentric 23. A hydraulic vmachine comprising a.- valve plate having annularly arranged inorts, a cylinder barrel mounted for rotatlon with respect thereto having axially arranged'cylinders of greater diameter than the radial width of the ports and ports leading from saidcylinders to the .valve plate ports, said cylinder ports where A they discharge into the' valve plate ports be-A ing of substantially the same radial width as such ports and being rounded at their ends by radial lines and at their sides by concentric circles and narrow dividing walls -between said ports, the cross sectional -ar'ea ofeach cylinder port atthe point where it is lntersected by the plane of the valve plate being larger than ythe' 'cross sectional area of its respective cylinder.

24. A hydraulic machine comprising a valve plate having annularly arranged-.in-

nuiV

take and exhaust ports, Va cylinder barrel mounted. for rotation with respect thereto having axially arrangedcylinders of greaterdiameter than the radial width of the ports' and ports leading from said vcylinders to the valve plate ports, said cylinder Vports where they discharge intothe valve plate ports being of substantially theI same radial width as such ports and being bounded at'their ends by radial lines and at their sides by concentric circles, the cross sectional area of each cylinder port at the point where it 1s intersected by the plane of the valve plate being larger than the cross sectional area of its respective cylinder.

25. A hydraulic machine comprising a valve plate having annularly arranged iny "take and exhaust ports, a cylinder barrel mounted for rotation with respect thereto having axially arran ed cylinders and ports leading from said cylinders to the valve plate ports, said 'cylinder ports where they discharge into the valve plate ports being of substantially the same radial Width as such ports andbein bounded fat their ends b y radial lllnes an at their sides by concentric circles and narrow dividing walls between said cylinder ports, the cross sectional area of each'cylinder port at the point where itl is intersected by the plane of the valve plate being larger than the cross sectional area of its respective cylinder.

26. A yhydraulic machine comprising a valve plate having annularly arranged intake and exhaust ports, a cylinder barrel mounted for rotation with respect thereto having axially arranged cyllnders andports Iwhere they` discharge into the valve plate ports of substantially the same radial width as' the valve plate ports and being bounded at their` ends by radial lines and kat their 'sides lby concentric circles, the cross sectional area of each cylinder port at the point Where it is intersected by the plane of the valve plate being larger than the cross sectional area of its respective cylinder.

27. In a hydraulic, transmission having .pump cylinders, pistons therein and means for operating them, motor cylinders, pistons therein and a member driven thereby, an/oil'- tight housing containing thecylinders and moving parts, 'a reservoir 1n communication with said housing and means responsive to the operating'ineans ofthe pump cylinders for forcing fluid from said reservoir into said housing.

28. yIn a hydraulic transmissionl having pump cylinders, pistons therein and means for operating them, motor cylinders, pistons therein and a member driven thereby, an oiltight housing containing the cylinders and moving parts, a reservoir in communication with said housin andmeans responsive to the operation cfg the pump cylinders for forcing fluid frein said' reservoir into said housing and a/"vpressure relief discharge valve controlling the, discharge\of fluid from said housing'v back to said. reservoir.

29. A hydraulic transmission lcomprising aclosedA chamber, power transmitting means contained therein, a housing comprising a series of separate assembly casing parts and means for holding them together, packing surfaces between them, said housing containing the chamber, a reservoir also within said housing, bleeder passages disposed within said packin surfaces. between the pressure side and t e holding 'means and connections, between said. bleeder passages andthe reservoir. i

30. A Vhydraulic transmission comprising a closed chamber, power transmitting means contained therein, a housing comprising a series of separate assembly casing parts and means for holding them together, packing` 4surfaces'between them, said housing containing the chamber, a reservoir also within said housing, bleeder passages disposed within said. packing surfaces between the pressure side and the holding 4means and connections between said bleeder passages and the reservoir and means for forcing oil from said reservoir into said closed chamber.

31'. A hydraulic transmission comprising a closed chamber, power transmitting means contained therein', a housin comprising a Vseries of separated assembly casing parts and means for holding them together, packing .surfaces between them, said housing ,containing the chamber,4 al reservoir also within said housing, bleeder passa es disposed within saidf packing surfaces etween the pressure sideA and the holdin means and connections vbetween said blee er passages and the reservoir and means for forcing oil from said reservoir into said closed chamber and meansfor controlling the discharge of 33. In a hydraulic-machine a valve plate, I'

a sleeve pro]ecting therefrom, a-shaft rota tably mounted therein, a cylinder barrel Arotatably mounted thereon, a housing for. the shaft, sleeve and barrel, a thrust bearing interposed between saidshaft andvsaid housing and a thrust connection between' said shaft and said cylinder. barrel, said thrust connection and 'thrust bearing each having vspherical bearing surfaces to permit relative displacementof the parts without binding. v

34. Inahydraulic machine an apertured valve plate, a sleeveprojecting outwardly therefrom, ahollow shaft rotatably mountdit@ ed therein, a cylinder barrel rotatably mounted on the sleeve, a connection between the apertures inthe valve plate and the interior of the hollow shaft, a thrust plunger mounted on said shaft, a cylinder in ywhich it is mounted, a connection between the cylinder and the interior of the shaft and a thrust connection between the shaft and the cylinder barrel.

In a hydraulic machie av packing joint between. opposed members comprising smooth contacting surfaces means for holding said surfaces together the joint between said members'being exposed on one side to a high and on the other side to a low pressure a bleeding duct located between such surfaces and thus between the areas of high and low pressure and a bleeder pipe communicating with such duct a storage reservoir in which such pipe discharges.

36. A housing, a shaft therein, a sleeve in rotatable engagement with the shaft, a cylinder therein, a self-alining bearingbetween the sleefe and the housing, a plunger mounted on the shaft in said cylinder and means for exerting a pressure within said cylinder against said plunger. fr 37. In a hydraulic transmission a valve plate having exhaust and intake ports, a hub centrally supported by said plate, hollow shafts contained rotatably within said hub, a plug withinfsaid hub between the ends of said shafts, a passage connecting said plug and each of said ports, tubular members extending from said plug and projecting into the ends of each of said shafts, said shafts being hollow, plungers on said shafts, thrust cylinders surrounding said shafts in which said plungers are located and al communication between the interior of said shafts and Y the interior of said cylinders.

38. A hydraulic transmission comprising a motor and pump, a'pressure' chamber contained within and connecting them, av closed housing surrounding them, and means for keeping said housingconstantly full of -oil under pressure, and for circulating said oilthrough said housing, said means compris-l ing a reservoir and means lfor pumping oill from the reservoir inte. said' housing.

40. vrA; hydraulic transmission comprising a motorand pump, a pressurel chamber contained within andconnecting them,-a closed housing surrounding them, and means for keeping said shousing' constantly full o f oil under pressure, and. for' circulating said oil through sai-d housing, said means comprising a reservoir and means for pumping oil from the reservoir into said housing, and

pressure relief means discharging from said under pressure, and for circulating said oil through said housing, said means comprising a reservoir and means for pumping oil from the reservoir into said housing, and pressure relief means discharging from said housing to said reservoir, said pressure relief being provided with means responsive to variations in the pressure of the oil. in the housing for controlling -the amount of oil discharged therethrough.

42. In a hydraulic transmission a fixed ported valve plate, a cylinderbarrel mounted for rotation thereon containing a plurality of cylinders and discharge passages leading therefrom, said passages extending to and controlled by the valve plate, pistons and means for reciprocating them within said cylinders toward and from the valve plate, the .relative areas of the cylinders, the discharge passages at the valve plate and the bearing surfaces between the barrel and the plate being such that the-forceexerted by the pistonsis insuiiicient to hold the barrelV `Iirn'ily against the plate and separate pres 'valve plate, the relative areas of lthe cylinders, the discharge passages at the valve plate and the bearing surfaces between the barrel and the plate being such that the forceexerted by the pistons is insuiicient to hold the barrel. firmly against .the plate, means separate from the cylinder barrel for holding it against the valve plate.

44. In a hydraulicv transmission a fixed ported valve plate, a cylinder barrel mounted for rotation thereon containing a plurality of cylinders and discharge passages leading therefrom, saidpassagesextendlng to and controlled bythe valve plate, pistons and means for reciprocating them within said cylinders toward andifrom the val-ve plate,

plate, a cylinder barrel.

the relative areas of the cylinders, the discharge passages at the valve plate and the -bearing; surfaces between the barrel and the i' plate being such that the force exerted by the pistons is' insuilicient to hold the barrel firmly against the plate, `hydraulic -means separate -f-rom the cylinder barrel for holding it against the valve plate.

45. In a hydraulic transmission a' fixed ported valve plate, -a cylinder barrel mounted .for rotation thereon containing a plurality of cylinders and discharge passages leading therefrom, said passages extending to and controlled by the valve plate, pistons and the 'means Afor reciprocating them within said cylinders toward and from the valve plate,

the lre'lative areas of the cylinders, the discharge lpassages at the valve plate andthe bearing surfaces between the barrel and the plate being such1that the force exerted by stons is insuicient to hold the barrel firm y against the plate, hydraulic means responsive to the conditions prevailing within' the cylinders and associate parts for holdin the cylinder barrel firmly against the va ve late.

46. n a hydraulic transmission la fixed ported valve plate, a cylinder barrel mounted4 for rotation thereon containing a plurality of cylinders and discharge passages leadin therefrom, said passages extending to an controlled bythe valve plate, pistons and meanslforv reciprocatingthem within said cylinders toward and from the valve plate,

the relative areas of the cylinders, the dischargepassages at the valve plate and the bearing surfaces between the barrel and the plate. being such that the force exerted by the pistons is insuicient to hold the barrel firm y against the plate,'hydraulic means rel sponsive to the conditions prevailing within a 'cylinder in whichv it is mounte draulic connection between theinterior` ofthe cylinders and associate parts for holdin thecylinder barrel firmly against the va ve plate, said means comprising a (plunger,

-- said cylinder and the interior of the cylinder barrel. f

.47. In a hydraulic. transmission a hydraulic system comprisin aported valve plate, a cylinder barrel, a s aft about which the barrel is mounted, and in response to which it` turns and operating members V mounted' for movement within said cylinder barrel, means surrounding said shaft .removed from thev barrel but communicating therewith, for holding the'barrel against the .valve plate, said means comprising aplunger, a'cylinde'r in which it 'rec1procates,. a communication between such means 'and the system com rising a central' channel through the "Said s aa through. which hydraulic pressure is transmitted from the lsystem to the fcylinder.- 4 -1 o 48.4 In a hydraulic ltransmlssion a .fixed l e. valve plate with, or'ts formed therein and a i valve face, a "cy inder vbarrel mounted for -said discharge passages, orts and valve face being so larve that iydraulic pressure within the cyllnders will not hold the barrel vagainst the valve face, and means removed from the barrel for holding barrel against the valve face.

49. A hydraulic transmission comprising a valve plate having an annular valve face with ports therein', a cylinder barrel havingv a corresponding annular valve face, axially arranged cylinders, with means for forcing fluid under hydraulic pressure from the cylinders and valve' ports, the valve faces being of such areaA that the hydraulic pressure within the cylinders is not suflicient to maintain them in contact, auxiliary means for maintaining valve faces in contact and cylinder ports from the respective cylinders to the valve face bounded at their ends b concentric circles and radial lines, where y the maximum port area is obtained with the minimum valve seat area, equal widths of oil seal surfaces beingmaintained all around each cylinder port.

50. A hydraulic transmission comprising a valve plate having an annular valve face with ports therein, a cylinder barrel having a corresponding annular valve face, axially arranged cylinders, with means yfor forcing fluid under'hydraulic pressure from the cyl-1 inders and valve ports, the valve faces being of such area that the hydraulic pressure within the cylinders is not sufficient to mai-ntain them in contact and cylinder ports from the respective cylinders to the valve face being maintained all around each cylinderl port, the width of the oil seal surfaces being suliicient only to prevent appreciable outflow of oil.

51. A hydraulic transmission having a rotar cylinder barrel, a driver secured thereto an swash plate, a universal driving joint for the swash plate comprising 'two rings articulated respectively to the barrel con trolling driver and swash plate and articulated to each other on an axis transverse to the axes of articulation between the rings and the barrel and swash plate.

52. vA hydraulic transmission having a swash plate and cylinder barrelfand means comprising a shaft, a driver "secured to the shaft and directly driving the barrel and a universal joint between thexiriver and swashl .plate for driving one from the other at a constant angular velocity.

53. A hydraulic transmission having a l holding the bearing end of said connecting rod to prevent backlash. v

54. Apiston, a cylinder in which it reciprocates, a driving member, a connecting rod interposed between the driving member-and the cylinder, a spherical bearing at one end of the connecting rod and means for holding said spherical `nearing yieldingly in snug operative position.

55. A driving member comprising a rotary swash plate, a series-of bearing blocks therein, a series of connecting rods mounted one in each of said bearing blocks and a spring harness mounted in the driving member for yieldingly taking up the backlash between the bearing blocks and the connecting rod ends.

56. A hydraulic transmission having an oil tight housing, joints in the wall'of said housing, bleeder ducts within said joints, a reservoir outside ofy said housing, pipes leading from said bleeder ducts to said reservoir, means for pumping a fluid from said reservoir into said housing and maintaining a predetermined pressure within said housing.

57. A hydraulic tranmission having an oil tight housing, joints in the wall of said housing, bleeder ducts-within said joints, a reservoir outside of said housing, pipes leading from said bleeder ducts tol said reservoir, means for pumping ai Huid from said reservoir into said housing and maintaining a predetermined pressure within said housing and means for cooling oil during its passage through said pipes.

58. A hydraulic tranmission mechanism, having a power pump mounted in a closed operating chamber, said pump comprising a high pressure port, ,a low pressure port and ,a passage from operating chamber into said low pressure port whereby leakage from the high pressure port and cylinders communieating therewith is returned into the low pressure port and means for maintaining pressure in the operating chamber.v

l59. A hydraulic transmission mechanism, having a power pump mounted in a closed 2 operating-chamber, said pump comprising a high pressure port, a low pressure port and a 'passage from operating chamber into said low pressure port whereby leakage from the high, pressure port and vcylinders communicating therewith is forced back into the low pressure port and means for maintaining pressure in the operating chamber. l

60.\ A hydraulic transmission, having a power pump mounted in a closed operating chamber, said pump comprising a high pressure port and a group of cylinders communichamber, Asaid pump Comprising a high pres- I sure port and a group of cylinders communieating therewith, a low pressure port and a group of cylinders communicating therewith, and a passage from operating chamber into said-low pressure port through which leakage from the high pressure port and cylinders is returned into the ylow pressure port and means for maintaining pressure in the operatingl chamber.

62. A hydraulic transmission mechanism,

having a power pump mounted in a closed operating chamber, said pump comprising a high pressure 'port and a plunger, driving mechanism and a connecting rod, a low pressure port, a passage from operating chamber to low pressure port and spring harness to prevent back-lash in the plunger movement,

. whereby the excess o .fgpressure inthe operating chamber above pressure in low pressure port necessary to force the leakage into the low pressure port. may be maintained without causing loss of plunger movement.

63. In4 a hydraulic transmission mechanism, a casing dividing the contained liquid into three zones of varying pressure, a power pump operating in the high pressure and intermediate pressure zones, and another pump operating between the intermediate pressure and lower pressure zone, said pump adapted to maintain the pressure in the intermediate pressure zone. l

64.- A hydraulic transmission mechanism, comprising a casing, a power pump and .anauxiliary pump, so arranged that the contained liquid is separated into three pressure zones', the total combined volume of the:

. means for maintaining the pressure in the l intermediate zone.

65. A hydraulic transmission mechanism comprising a casing, a power pump and an auxiliary pump, so arranged that thecontained liquid is separated -into three pres` sure zones, the'total combined volumeof the highest and intermediate pressure zones being vconstant and limited by a closed operating chamber, and an auxiliary pump adapted to returnthe leakage from the lowest pressure zone to the intermediate pressure zone, and adapted thereby to maintain the pressure in thel intermediate pressure zone.

66. In a hydraulic transmission, a casing dividing Vthe contained liquid into ,three zones of varying pressures,a power pump operating in the hlgh pressure and intermediate yessure zone, and another pump oper.- ating tween the intermediate pressure and low pressure zone,

intermediate and low ressure zone, vsaid wall being pierced only y leakage passagesy and by the auxiliary pump passage.

Signed at .Mi1waukee, county of Miland a wall between saidv waukee and State of-Wisconsin, this 7 day '115 of February, 1916.

WALTER FERRIS. 'In the presence of Witnesses:

GEO. H. RONDEAU, KATHRYN OCONNELL. .Signed at South Milwaukee, county of Milwaukee and State of Wisconsin, this 7 day of February, 1916.

WILLIAM-E. MAGIE. In the presence of witnesses:

GEO. H. RoNDnAU, KATHRYN OCoNNnLL.

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