US2312417A - Pump, compressor, or hydraulic motor - Google Patents

Description

March 2,. 1943.

D. G. JONES PUMP, COMPRESSOR OR HYDRAULIC MOTOR Filed May 7, 1940 4 Sheets-Sheet 1 March 2, 1943. D. G. JONES- 2,312,417

PUMP, COMPRESSOR OR HYDRAULIC MOTOR Filed May '7, 1940 4 Sheets-Sheet 2 lue/2&5, 1 M G 75/026 Jag) March 2, 1943. D. ca. JONES ,3 ,4 7

PUMP COMPRESSOR OR HYDRAULIC MOTOR Filed May '7, 1940 4 Sheets-Sheet 3 March 2, 1943. D. G. JONES- 2,312,417

PUMP, COMPRESSOR OR HYDRAULIC MOTOR Patented Mar. 2, 1943 ;PUMP, COMPRESSOR, R HYDRAULIC oron Dudley George Jones, Aldwych,London,-England ApplicationtMayY, 1940,.Serial N0. 333,866 In Great hBritain. May-8,1939

The present invention has reference toanimproved construction of pump, compressor or hydraulic motor comprising two cylinder blocks rotatably mounted in a casing at an angle to each other with an end of each block adjacent to an end of the other and angular pistons arranged one end of each piston in a cylinder in one block andthe other end in a cylinder in the other block, said pump, compressor or motor being of comparatively light weight and size and giving high efficiency with comparatively low cost of production.

The primary feature of the present invention consists in making the main casing of the pump or motor in parts detachably joined together in the plane containing the axesof the cylinder blocks.

The blocks are preferably supported at their ends by bearings directly mounted on the casing.

When the invention is applied to a pump driving worm Wheels for the cylinder blocks areattached to theblocks intermediately of the ends thereof.

When the invention is applied to a, motorone block is provided with the drive shaftgand-the drive is preferably transmitted from thisblock to the other through a bevel wheel on the directly driven block in mesh with abevel wheel on the other block. The bevel wheels may be -cmitted in which case the pistons transmit the drive from block to block.

In all forms of the invention each block is preferably provided at its outer end with; an-in tegral valve head whilst the outer end of the valve head has an integralbearing spigot, the valve heads and bearing spigots being arranged within housings secured to the main casing. Such an arrangement has the advantage that the'pump or compressor may be run in either direction without the possibility :of the valve heads becoming loose with respect to their blocks whilst the spigots and anti-friction bearings around them provide firm supports forthe outer ends of the blocks, which supports'work in conjunction with the bearings at the ends of'the blocks. If the machine bedesigned'for use as a motor one of the spigots is extended or is provided with an extension to form thedrive shaft thereof, said extension being'passed' through a gland or fluid seal mounted on the appropriate valve housing.

A pump and a hydraulic motor will now be described with reference .to the accompanying drawings wherein:

Fig. 1 is mainly a sectional elevationtin az-vertical plane passing through the axes of-the cylinder blocks of a pump;

Fig.2 isa sectional view on the line 11-11, Fig. 1;

Fig; 3 isa sectional elevation in a vertical plane passing through the axes-of the cylinder blocks of a hydraulic-motor; and

Fig. 4. is an end view of the said motor.

The pump illustrated in Figs. 1 and 2 has a casing comprising two parts I and 2 of mating shape adapted to meet in the plane (indicated by the line AB) containing the axes of the cylinder blocks3 and 4. .The said parts I and 2 are flanged at their meetingedges, said flanges being indicated by :5 and areheld together by bolts andnutsfi passing through bosses on the flanges.

The casing parts are enlargedat Ttoprovide wells for Worm wheels 8. The part I is provided with a flange 9 enabling it to be fixed to-an aero engine or the likeand the walls I. of the wells 1. on the part I arecarried round to a cylindrical socket") integral with the flange 9. Thesaid walls "I, in addition to providingthe.w el-ls,:thus provide means strongly securing the flangez9 to the part I.

Each cylinder block (3 or iyhas fourbores H containingthe ends-0f angular pistons l2, synchronous rotation; of the blocks- 3, 4 causing the piston ends to reciprocate in ,the manner described, for example, in United :States Patent No. 2 111652. The worm wheels-8are comprised in the means for effecting the simultaneous rotation of t he blocks. Each wheel has four inwardly directed centering lugs l3 and each block an external flange I 4. Bolts-t5- extend through the lugs and the-flanges to secure the wheels to their respective blocks, said bolts 15, which are provided with nuts 16, being-parallel with .and arranged around the axes of the blocks. 7

At-this pointI would mention that the teeth of thevgears must be located in mating relationship-with respect to their common driving worm Hand must be in correct relationship with the bores of the cylinders in order that theraxes of corresponding bores may lie exactly in thejsame plane. If the worm wheel teeth were cut in.

flanges on the cylinder block'castings it would be necessary to efiecttheboring of the castings subsequently to the gear cutting as it; is commerciallyimpossible to startecutting a tooth iatone particular point. The said procedure would be an expensive machining method and in the event of h lind or ioperati n exposing flaws in m -cyl nde .blps thfle astingxwouldhalter-. 20

wheels are clamped to the flanges l4 and the se-' curing holes for the bolts l5 drilled and reamed and the said bolts fitted.

The blocks 3 and 4 are rotatably supported in the casing formed by the parts l and 2 by bearsaid bearings being run direct onto the casing so as to expand and contract with it. Owing to this location of the bearings |8 with respect to] the blocks each block is supported at opposite sides of its wheel 8.

Valve heads as I9 are integral with the blocks 3, 4 at the outer ends thereof and the outer ends of the heads are integral with bearing spigots as 23. ports 22 serving for the inflow and the outflow of fluid to and from the bores H and the housings 23 in which the said valves are arranged have corresponding inlet and outlet conduits 24 and 25 With which the ports 22 successively communicate during rotation of the blocks, conduits 24 being in communication with connecting nipples as 25 on the housings 23 and conduits 25 with nipples 21 on the said housings.

The housings 23 in addition to enclosing the valve heads l9 are fashioned to support antifriction bearings as 28 fixed to the spigots as 28. The fixing means for each bearing comprises a nut 29 adapted to press the inner race of the bearing into close contact with a stout washer 30 at the opposite side of the said race, said washer seating on a shoulder provided by thereduced diameter of the spigot 28 with respect to the valve head IS. The nut 29 is secured to the spigot by a pin. Caps 3| are located on the housings 23 and the said housings and the caps are secured in position by studs 32 extending through the caps and bores around the housings and engaging with the ends of the casing formed by the parts 2.

The valve heads l9 are smaller in diameter than the blocks 3, 4 and washers as 33 are located on the resulting step. The washers as 33 between the outer ends of the blocks and the adjacent parts of the housings 23 and the washers 30 at the outer ends of the valve heads l9 oppositely contact with the ends of the bores containing the heads |9 to prevent axial movement'of the blocks. Furthermore, outfiowing working fluid escaping through the working clearances between the valve heads l9 and the casings 23 presses against the upper surface of the washers 33 and that part of the under-sur- The heads l9 have conduits 2| with lateral face of the washers 30 projecting from the heads H H! so that, the surface of washer 33 on which the fluid acts being larger than the surface of the washer 39 on'which the fluid acts, the blocks are thrust inwardly against the outward thrust of the pistons l2 when discharging fluid from the pump or compressor. The relative proportion'of the effective faces of the washers 30 and 33 is such that the thrust of the pistons on the blocks is substantially nullified. The washers 33 are pinned to the cylinder blocks to prevent rotation between the washers and the blocks.

If the working fluid is oil it lubricates the machine by seeping through the working clearances between the bearings and rotatable parts and through other spaces. Most of the lubrication effected in this manner is by the oil which flows along the working clearances between the valve heads l9 and the housings 23. Oil which act: on the washers 30 flows upwardly through the bearings 28, downwardly through .the central bores 34 of the blocks to the bottom of the main casing, upwardly through the clearance between the lower bearings l8 and the lower ends of the blocks and into the housing 35 for the worm Oil which has acted on the washers 33 passes '15 ings l8 at the outer and inner ends of the blocks,

the upper bearings I8, enters the wells 1 and passes into the housing 35. From the housing the oil is conducted back to the suction tank (not shown) by means of a pipe connected to the housing at boss 36.

The housing 35 is formed by appropriately fashioned portions 35 and 35 of the parts and 2, respectively. The portions 35 merge into the socket I8 and'the parts 35 comprise a recess 37.

The recess 31 contains a roller bearing 38 supporting one end of the spindle 39 of the worm 1. This bearing 38 is of a type permitting longitudinal movement of its inner race and the rollers with respect to its outer race, the object being to permit of expansion of the Worm shaft. The socket I0 contains a double thrust ball bearing 40 supporting the other or driving end of the shaft 39, the inner race of the bearing being shrunk onto the said shaft.

A sealing gland is provided in a sleeve 4| adapted to screw into the outer end of the socket It], said sleeve locking the bearing 40 in position in the socket. The members of the sealing gland comprise a stepped collar 42 which is an interference fit in the hollow of the sleeve 4|. The inner or thin-walled end of the collar 42 presses the outer margin of an annular membrane 43 against a circular rib 44 in the sleeve 4| and so secures the membrane 43 within the gland. A ring 45 is slidably arranged within the collar 42. Pockets 46 in the collar 42 and the ring 45 contain springs 41 which normally press the rings 45 to the right. The ring 45 is stepped at a part adapted to contact with the inner marginal portion of the membrane 43 and a second ring 48 is located at the opposite inner margin of the said membrane. Thus, the pressure of the springs 41 causes the inner part of the membrane 43 to be gripped between the rings 45 and 48, the ring 48 yieldingly thrusting against the inner race of the bearing 40, owing to the spring action. The ring 48 is a sealing nose and, in conjunction with the diaphragm 43, prevents leakage of fluid alo'ng'a collar 49 shrunk onto the shaft 39 and located inside the collar 42 and the ring 45. 'Unintentional rota: tion between the sleeve 4| and the socket II] is prevented by a plug 50 forced into contact with the screw-threaded part of the sleeve by means of a grub screw 5| in a nipple 52; said plug 50 being in the bottom of the bore'of the nipple. The inner members of the sealing gland are prevented from rotating by means of pins as 53.

If desired a second sealing gland substantially similar in construction to that just described may be provided around the left hand'end (Fig. 2) of the shaft 39 to ensure that oil" cannot flow along the shaft either from the engine to which the pump is secured or'fromthe pum to theengine. I I

A pump constructed as herein described with reference to the accompanying drawings gives almost continuous flow, there being four discharges of each cylinder block per revolution, and it is found that the flow of fluid in the pump suction pipe is almost continuous. Therefore, liquid flows into the cylinders on the suction strokes without difliculty and high piston speeds can be used without cavitation occurring. Furthermore, the high piston speed makes sealing devices unnecessary as liquid does not have time to leak down the working clearances between the pistons and the cylinder bores. The pump has also been found to give highly satisfactory results at low piston speeds.

The motor illustrated in Figs. 3 and 4 is analogous to the pump already described and corresponding parts have been given like numbers. The primary differences are, however, the provision of bevel wheels 54 instead of the worm wheels 8, the omission of the worm l1 and the corresponding fashioning of the casing to support the shaft of the worm, the provision on one of the spigots 20 of a drive shaft 55, and the location of the fixing flange 9 and the sealing gland around the spigot end of the shaft 55.

The bevel wheels 54 inter-mesh so that the blocks 3 and 4 are compelled to rotate in synchronism, said blocks being supported at opposite sides of the wheels 54 by the bearings l8 in much the samemanner as described with reference to Figs. 1 and 2.

The shaft 55 and the corresponding spigot 20 are integral in order to give strength and, more particularly, to enable the shaft to be rotated in either direction without fear of working loose from the said spigot. The flange 9 is secured to the valve housing 23 by studs 32.

It will now be clear that upon pressure fluid being introduced to the cylinder bores by way of the nipples as 26 and conduits 24 the piston ends in the cylinder bores communicating with the said conduits will be subjected to the pressure and urged outwardly with the result that the blocks will rotate and successive pistons will be subjected to the pressure whereby the rotation is maintained, the fluid exhausting by way of the conduits 25 and connecting nipples 21.

Instead of thrust surfaces larger than the surface of the washers 30 being provided by means of added washers as 33, Fig. 1, the blocks in Fig. 3 are shouldered to provide surfaces equivalent to those of the washers 33.

The bore 34 in the block, valve head and spigot with which the shaft 55 is integral is placed in communication with the oil seeping through the working space between the spigot and part of the valve housing 23 by the provision of a lateral duct 56 in the spigot and slots 51 in the outer face of the adjacent washer 30, said spigot being grooved at 58 to provide a drain for the oil communicating with the duct 56. Oil that has effected the requisite lubrication is conducted back to the suction tank (not shown) by means of piping connected to the wells formed by the enlargements I by Way of nipples as 59. The other block may have a duct as 56 for the same purpose if it is required to close the outer end of the bore 34.

In order to obtain the requisite strength between the shaft and the block these elements are, as previously stated integral with each other and in addition are made of steel or steel alloy for strength. In order, therefore, to prevent seizing between the said block and the piston ends working in it gun-metal sleeves 6|] or sleeves of any other suitable alloy are shrunk or otherwise fltted to the said ends. The other block is of gun-metal or the like and the corresponding piston ends of steel.

The pistons of the pump or compressor illustrated in Figs. 1 and 2 may be provided with the sleeves as 60 for working in a cylinder block of steel or the like whilst the other block may be of gun-metal or the like.

Ball or roller bearings may be used in place of the bearings l8.

A pump and a motor each with four cylinders has been described: each may, however, have three, five or more cylinders.

What I claim is:

1. A fluid engine, comprising a casing, two cylinder blocks in said casing at an angle to each other, the blocks having projecting elements between their ends, bearings directly mounted in the casing circumscribing the ends of the blocks, angular pistons arranged one end of each piston in a cylinder in one block and the other end of each piston in a cylinder in the other block, driving worm wheels for the cylinder blocks circumscribing the blocks between said bearings, said driving worm wheels having coacting parts enabling studs parallel with and around the axes of the blocks to secure the wheels to the blocks, and a driving worm in mesh with said driving worm wheels.

2. A construction as defined in claim 1, wherein each cylinder block has a valve head, with each valve head having a radial outlet conduit with a valve housing having a corresponding conduit, each valve head being shouldered at parts adjacent to the opposite ends and provided with a thrust surface at its cylinder end and a smaller thrust surface at its opposite end, whereby pressure fluid leaking through the working clearance between the valve head and its housing and pressing against the said thrust surfaces acts with greater effect on the larger surface than on the smaller one in opposition to the thrust of the pistons, the thrust surfaces being proportioned to substantially nullify the piston thrust on the blocks.

DUDLEY GEORGE JONES.

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