US2917243A - Tank washing apparatus - Google Patents

Description

Dec. 15, 1959 v. LIONE 2,917,243

TANK WASHING APPARATUS Filed Aug. 5, 1957 4 Sheets-Sheet 1 FIG.- 1

Leonard V. Lione Inventor By yw Attorney Dec. 15, 1959 L. v. LIONE 2,917,243

TANK WASHING APPARATUS Filed Aug. 5, 1957 4 Sheets-Sheet 2 FIG.'6

Leonard V. Lione Inventor By /67 Attorney Dec. 15, 1959 v, LIQNE 2,917,243

TANK WASHING APPARATUS Filed Aug. 5, 1957 4 Sheets-Sheet 3 lOlc lOlb Leohqrd V. Lione Inventor Dec. 15, 1959 Filed Aug. 5, 1957 L. v. LIONE 2,917,243

TANK WASHING APPARATUS 4 Sheets-Sheet 4 Leonard V. Lione Inventor By W Attorney TANK WASHING APPARATUS Leonard V. Lione, Fanwood, N.J., assignor to Butterworth System, Inc., a corporation of Delaware Application August 5, 1957, Serial No. 676,110

5 Claims. (Cl. 239-227) The present invention relates to an apparatus particularly adapted for cleaning the interior wall surfaces of a container vessel. More particularly, the invention relates to a tank washing apparatus providing for the discharge of high pressure jet streams of a cleaning liquid so as to impinge against the interior'wall surfaces of such container vessel. The invention further relates to such an apparatus wherein a nozzle structure is driven through an overriding clutch mechanism and a similar mechanism is provided in combination with support means for said structure. Still more specifically, the invention relates to a tank washing apparatus wherein the operating structure is made up of a series of substantially self contained individual operating units mounted in relatively spaced relation along a common axis to form a unitary assembly, and a nozzle structure mounted on and driven through said assembled units.

In conventional tank washing apparatus of the char;

acter contemplated, a nozzle structure is mounted on a vertically suspended housing for rotation about a horizontal axis, while the housing is rotated about a vertical axis. Conventionally, also, the housing contains a water motor, or impeller, driving speed reduction gears for rotation of the nozzle and housing. In some devices, the gears and other parts of the driving means are contained within the housing, while in most such devices the operating parts and gears are mounted externally, and/or supported in bearings havinglarge clearances to provide for lubrication and/or cooling by water or other cleaning liquids escaping therethrough. v

In the first mentioned apparatus design difiiculties are encountered in the original manufacture and assembly of the apparatus. In order to maintain a lubricated drive means and gear box, effective seals must be established, and leakage of the cleaning liquid eifectively limited. These requirements are difiicult to attain in the limited space available. They are also complicated by the fact that cleaning liquid pressures above ,150

p.s.i.g. may be attained in the fiow passages through the housing.

In the second design form, the exposed mechanisms and gearing are most liable to damage. Also, because of the loosely fitted operating parts, at even moderate pressures leakage is so excessive that effectiveness of the nozzle streams is considerably reduced.

A further difficulty is experienced with conventional apparatus forms where openings provided for introduction of the assembled device are small, and require precise alignment of the nozzle structure before introduction and removal. In such circumstances damage may occur through pressure exerted against reduction gear parts or otherwise. In another instance, while attaching means must be provided for rigid coupling to a cleaning liquid supply conduit, during attachment this means must be free to rotate with reference to the housing, and vice versa, without excessive leakage under the operating pressures.

It is an object of the present invention to provide a- "ice units whereby to facilitate initial construction and subsequent service or repair. In addition, it is an object of this invention to provide means whereby parts of the assembly required for fixed or interacting relative relation in service may be relieved of such relationships when the assembly is not in service.

The invention and its objects may be more fully understood from the following description, especially when it is read in conjunction with the accompanying drawings, of which:

Fig. 1 is a view in elevation from the nominal front of the apparatus with parts broken away or removed to show certain essential features of construction contem plated according to the invention;

Fig. 2 is a plan view looking down on the apparatus as illustrated in Fig. 1;

Fig. 3 is a view of the apparatus in longitudinal section with parts broken away and in elevation taken generally along the line IIIIII of Fig. 2.

Fig. 4 is a view in horizontal section taken along the line IV-IV of Fig. 3, with parts shown in plan view;

Fig. 5 is an exploded view of a portion of the discharge nozzle structure as shown in Fig. 3, taken'substantially along the line V-V of Fig. 1 and including the overriding clutch and driving means therefor; and.

In the drawings, like parts are designated by the same:

numerals. Accordingly, the several figures will be referred to specifically by number only as required to' identify parts as shown in specific figures.

As shown, the apparatus is composed of a series of sub-assembly units including a gear case 1, an impeller case and nozzle structure support unit 2, a combined housing cap, support tube and coupling unit 3, and a nozzle structure 4. 3 are provided so as to be joined in superposed ascending order along a common axis and in spaced relation longitudinally thereof.

The gear case unit 1, as shown, is shaped to provide vertical side wall portions 11 of substantially horseshoe shape, wherein the ends, or quarters are connected by a flat vertical cross wall portion at the front of the case. The upper end, or top wall 13, matches the side wall peripheral conformation and is integral with such wall portions. The upper surface of the gear case unit is stepped upwardly from the flat wall portion 12 in two steps. Primarily this is to provide a maximum spacing between it and the bottom wall portion 45 of the impeller case 2 next above in the complete assembly, and

. with the cross wall 12. Thus, these bosses provide an enclosure open at the cross wall end. In addition, each Patented Dec. 15, 1959 Also as shown, the units 1, 2, and' V 3 boss terminates at its upperend in a plane common to that of said platformed boss, and further is drilled and tapped.

The top end wall 13 of the gear case 1 further provides guide and'stop'means for proper location of the unit 2 next above. In the unit as shown, the guides take the form. of two oppositely disposed smaller bosses 16 and 17 inwardly of the peripheral bosses 15. Each of the bosses 16 and 17 is shouldered to provide curvilinear, inwardly facing vertical wall portions 16a and 17a respectively. The; inner side of theboss 14 is similarly shouldered'at 1 8, and on substantially the same radius. The function,

depth and radial focus of the shouldered portions 16a,

' tudinal axis of the complete assembly. Bearings 2th: and

b provide rotational guides for the shaft ends. The bearing 20b, disposed-in a suitable passageway defined in the upper end wall 13 is press fitted therein in fluid,

tight relation thereto. The upper end of the shaft is extended through the bearing above the. upper end wall and is rovided with a retainer seal'ZGc. The upper end of the shaft'20' also provides one part of a shaft coupling. As shown, this part is a recessed or grooved portion 20d adapted to receive a tongue provided on the lower end of another shaft section extended from the impeller case 2. The axis of the shaft 20 is also the focus of curvature for the shouldered portions 16a, 17a, and 18.

The worm 19 engages a worm wheel 21 mounted on a shaft22 driven thereby. This shaft is mounted on suitable bearings within. the case, one of which is contained in a cap 22a threadedin a receiving passageway provided in the case cross wall 12. The shaft 22 is at right angles to the shaft 20, and radially spaced therefrom. The shaft 22 also carries a spur gear 23 adapted to engage a meshing gear 24 mounted on a shaft 25 parallel to the shaft 22 and radially spaced from shaft 20 on the opposite side thereof from the shaft 22.

A boss 26 on the outer surface of cross wall 12 defines a passageway adapted to receive a combined shaft seal, bearing retainer and case bearing 27 for the shaft 25 adjacent its outer end. The inner end of the shaft 25 is supported by a suitable bearing in the case wall portion. 11. This end of the shaft 25 carries abevel or miter gear.

28, while the outer end extends through the element 27 to receive a spur gear pinion 29.

A fourth shaft31 is supported in a passageway 14a defined in the boss 14, and by means of a bearing and retainer seal assembly 32 adapted for threaded engagementin the passageway. The upper surface of the retainer seal is disposed substantially flush with the surface of the boss, and the upper end of the shaft flush with retainer surface. This'end of the shaft is provided with a threaded recess 31a, adapted to receive the threaded end ofanother shaft section as later set forth. The shaft 31 isdisposed so that its axis is in right angular intersecting relation to the axis of the shaft 25. A collar portion 31b suspends the shaft 31 on the bearings therefor. The lower end of the shaft supportsja miter gear 33 for meshed relation with the gear 28 on shaft 25. The lower end of the case 1 is moulded to a substantially circular contour and is provided with a removable sealed cover plate 34.

As illustrated by Figs. 1 and 3, the impeller case is next in the ascending order of the assembled units. This unit has a conformation substantially corresponding to that of the gear case 1, including horseshoe shaped side Wall portions 42, and a flat cross'wall portion 43. Top and bottom end wall portions 44 and 45 respectively are formed integrally with .the side wall and cross wall portions, and are flanged outwardly from the side wall portions of the case as indicated by numerals Za and 2b. The bottom end wall flange 2a is adapted to be seatedon the bosses 14 and 15 of the case and to be attached thereto .as

by the bolts shown. The upper end wall flange 2b is adapted to receive and be bolted to the lower end of the housing cap of unit 3.

The cross wall 43 is of substantially circular, peripheral contour, extending radially beyond the side wall and bottom end wall portions 42 and 45. Integral with the cross wall 43 is annular peripheral rim wall 46 extending outward therefrom at right angles to the surface, and a concentric axle tube 47, which extends outwardly beyond the rim. Between them, the rim wall 445 and the axle tube 47 define an annular recess with the obverse surface of the cross wall 43 forming the bottom thereof. In a lower sector of the cross wall 43, and displaced from a diameter thereof which is parallel to the assembly axis, the rim is thickened to provide a radial extension portion 46a. This portion defines a chamber having a central axis lying substantially in a circular line common to the major portion of the outer periphery of the rim wall 46. The chamber is of circular contour, opening through the reverse surfaceof the wall .43, and adapted to receive the outer end of .the geancase shaft 25 and the attached spur gear 29'. As shown, the extension 46a is also located so as to match the location'of the shaft 25 and gear 2? and to be concentric therewith. Means are provided to seal the boss 26 in the opening through the wall 43 and'the rim extension portion 46a. The chamber, by reason of its disposition also opens into the recess between the wall 43 and the axle tube 47. Spider vane portions 47a in the outer end of the tube 47 support a projecting flow diffuser element 48, and a nozzle support stub shaft and bearing 49.

As shown, the bottom wall 45 inclines downwardly at 45a to join the reverse surface of cross wall 43 substantially at a level corresponding with the juncture of the lower half of the axle tube 47 with the obverse surface of cross wall'43.

The case 2, defines an interior, substantially L-shaped, passageway 41 which opens at the upper end through the upper end wall portion 44 by way of an integral axial tubular portion 44a, and at the lower end through the cross wall 43, and the axle tube 47. Within the passageway 41, and centered on the axis of the assembled structure is an upstanding annular boss 45b, integral with the bottom end wall 45, providing a shaftway which opens through thebottom wall 45. A buttress web 51 connects the boss 45b with the wall portion 42.

The upper end of the tubular portion 44a is adapted to receive and rigidly retain a guide vane insert 52, wherein the vanes 53 are formed from a root 53a at the upper end to extend radially from a hub 52a to a rim 52b, and curved downwardly to a delivery edge 53b, the root and delivery edge each lying in a line related to the hub axis by an angle of about 45; the hub having an axis common to the case 2 and the assembled structure.

Also disposed concentric with the assembled structure is a drive shaft section 54, the upper end of which is received'for rotation in a bushing 55 mounted in the hub' 52a. The lower end of the shaft section 54 extends downwardly through the boss 45b and outwardly through the bottom wall 45, terminating in a coupling part 5411 adapted to engage and match the coupling part 20d of the gear case drive shaft 20. As shown the part 20d is a grooved end portion, while the part 54a is a tongue which fits the groove.

Intermediate the upper end of the boss 45b and the vaned hub 52a, a vaned impeller, including a'hub 56and impeller vanes 57, is mounted on the shaft 54, being fixed in relation to the shaft and supported thereon by a collar 54b. A bushed seal-bearing 58 for the shaft 54 is provided in upper end of the boss 45!), and expansion spring 59between the bearing 58 and collar 54b maintains the hub 56 in rotationable surfacecontact with the bearing 55,. while-exerting pressure against the seal-bearing and bushing assembly 58. A screwdriver slot 540 is provided in the upper endof the shaft 54. The impeller vanes .57

are curved downwardly from an upper edge 57a to a lower edge 57b in a direction opposite to that of the vanes 53, and with a slightly greater radius of curvature. The upper and lower edges of the vanes lie in a line at an angle to the hub axis which is substantially equal to the angular relationship of the vanes 53 to the hub 52a, whereby cleaning liquid is initially directed against the impeller vanes 57 by the guide vanes 53 at an optimum angle of about 90".

A portion 42a of the case side wall 42, opposite to the extension portion 46a of the cross wall 43, is enlarged and drilled longitudinally to form a shaftway 42b. This shaftway has an axis in right angular intersecting relation to the axis of the chamber in the extension portion 46a, and to the axis of gear case shaft 25. A shaft 62 disposed in this shaftway extends downwardly therethrough. The lower end 62a of the shaft is threaded for connection in the threaded recess in the upper end of gear case shaft 31 to be driven thereby. The shaft 62 is elongated, and the upper end 62b extends upwardly be yond the shaftway and extension portion 42a. The shaft carries a spur gear 63 at its upper end, and also is provided with a screwdriver receiving slotted portion 620 therein.

Referring again to the bottom wall 45, it is to be noted that the lower or outer face is milled about the periphery common to the flanged portion 2a thereof, and along a contour substantially conforming to that of the side Wall portions 42, whereby to produce an angular, shouldered peripheral recessed portion 64, having an inner vertical wall depth slightly less than the shouldered portions 16a, 17a and 18 provided in the bosses 16, 17, and 14 respectively, and a radius of curvature substantially equal to that of the shouldered portions 16a, 17a and 18. With the flange 2a in contact with the upper ends of the bosses 15 and 14, then the recessed wall 64 is engaged by the wall portions 16a and 17a to guide the case 2 into alignment with the case 1, with bolt holes in the flange 2a aligned with those in the bosses 15 and 14, the wall portion 64 being finally engaged by the shoulder Wall 18 acting as a stop therefor.

In the unit 3, the numeral 71 designates a support and cleaning liquid inlet tube having an enlarged lower end 72, internally and externally shouldered as at 73, and at 74 and 75 respectively, and defining an internal passageway 76c flared at its inner end to match the passageway 41 at the inner periphery of the annular shoulder 73. The tube 71 is sealed in rotative relation to the axial tubular portion 44a of the impeller case top Wall 44, by means of the annular seal ring 44b mounted and disposed as shown.

In the structure illustrated, the external shouldered portions 74 and 75 respectively provide mounting surfaces for an externally toothed ring gear 76, and the inner race 77 and rollers 77a of a two part conical roller hearing. The other conical raceway portion of the bearing is indicated by the numeral 78. The ring gear 76 is retained against longitudinal movement on the tube 71 by means of a spring retainer ring 79, and against rotation by means of a tooth portion 74a on shoulder 74, adapted to be re ceived and engaged by a recessed portion 76a in the ring gear 76. The raceway 77 is press fitted upon the tube 71.

The housing cap of the unit 3 is designated by the numeral 81. This is a substantially cup-shaped inverted cap element, having a wall portion 81:; defining a passage for the upper end of the tube 71, which, as shown, is

adapted to extend through such passageway in sealed,,

. 6 of the tube 71 in rotative surface relation, and the respective wall surface portions are sealed as by the seal ring 80. The shouldered portion in the cap 81 is adapted to receive the conical bearing raceway 78 in press fitted relation. Bosses such as indicated at 86 and 87 peripherally of the rim of the inverted cup shaped housing 81 are disposed and adapted to be received by the flange 2b in aligned relation to bolt holes therein for rigid connection of the case thereto. The bosses such as 86and 87, extend beyond the housing rim, whereby to provide spaced separation of the housing 81 from the flange 2b. 7

' Integral with the outer wall of the housing 81 there is formed a thickened radial extension 88. This ex: tension portion is drilled on an axis parallel to the central axis of the housing, and the assembly, to provide a shaftway 88a to receive the upper end 62b of the shaft 62, and a chambered portion 88b at the'upper end of the shaftway. This chambered portion opens through the inner wall of the housing into the chambered portion 81b, and is adapted to receive the spur gear 63 on the upper end of the shaft 62. The disposition of the chamber and the dimensions of the ring gear 76 and spur gear 63 are such as to provide for engagement between the gears. A threaded cap 89 provides a closure for the upper end of the shaftway and chamber.

Included in the sub-assembly 3 is a means for coupling the apparatus to a source of cleaning liquid, such as a hose or pipe, not shown. This means is composed of a color 91 and a male coupling element 92 exteriorly threaded for engagement by a coupling nut on a hose or pipe connection. The collar 91 and element 92 are joined by means such as bolts 920.

The collar 91 is freely fitted on the upper end of the tube.71, as is also the element 92. Each of the collar 91 and element 92 is formed with an annular shouldered portion 91a and 92a disposed for opposite facing rela-' tion when assembled on the tube 71, and the coupling element 92 is provided with an annular seal ring 9211 to engage'the outermost end of the tube 71. A ring portion 91b formed integrally with the collar 91 and extended radially there-from provides means for attaching a rope support and guide means.

The face of the shoulder 91a on collar 91 is provided with a series of notched portions 93 forming a corresponding series of teeth 94, wherein the tooth and notch side wall portions 95 are inclined at an angle'of between about 30 and about 60 to the clearance line of the teeth. The collar thus forms the primary element of an overriding clutch, wherein the secondary clutch element is an inwardly flanged annulus 96 adapted for threaded engagement with the upper end of the tube 71 between the shouldered portions 91a and 92a, and maintained in such engagement by a retainer ring 97. The lower edge of the annulus 96 is notched and toothed to match the upper surface of the shoulder 91a, the notch and tooth portions being designated by the numerals 98 and 99 respectively, and the inclined side Wall portions by the numeral 100. The shouldered portions 91a and 92a are spaced at a distance at least equal to the assembled distance between the surface of a tooth portion 99 and the upper surface of ring 97, plus the depth of a notch portion 93, whereby the crown surfaces of tooth portions 94 and 99 may be disposed substantially in a common plane.

The remaining sub-assembly unit is the nozzle structure 4, and the'means for driving the nozzle structure for rotation about the axle tube 47. Basically, the nozzle structure 4 is composed of an annular hub 101 having annular shouldered portion 102, wherein said hub is adapted for telescopic, journalled fit over the axle tube 47. Integral with the hub 101, are at least two nozzle portions 103 and 104 which, with the hub 101, forms a substantially offset T discharge conduit means. A recessed portion 101a internally of the hub is adapted to be received in sealed rotative relation to the flow diffuser element 48 and to be axially engaged by the outer end of the stub shaft 49, through an axially defined passage in the hub and radially recessed portion 1010. A cap 105 provides for threaded engagement with the threaded end of the shaft 49, and maintains the mounted relationship of the nozzle structure to the axial supports therefor. Set screws 105a prevent loosening of the cap 105.

A series of annular seals, including seals such as indicated by the numerals 106 and 107 are provided against liquid leakage from or into the related rotative joints. Also, where such seal is intended to hold against a positive pressure of liquid, as is the seal 106, provision is made to release such pressure intermediate the seal and the joint protected. Thus, in the nozzle structure 4, the face of the hub portion is provided with a series of passageways 108 defined therein so as to communicate with the joint between the nozzle and the axial diffuser portion 48 intermediate the seal 106 and the bearing 109. Additionally, to seal against the pressure of cleaning liquid passing into and through the nozzle structure 4, the axle tube 47 is provided with a pair of annular groove portions spaced longitudinally of the tube at the outer end thereof and adapted to receive seals 110 and 111. To relieve the pressure of liquid passing the first seal 110, and to discharge any such leakage, the hub 101 is provided with an annular groove portion 112 disposed so as to lie between the seals. Radial passageways 113, also defined in the hub 101, communicate between the groove portion 112 and the ambient atmosphere.

As shown in Fig. 3, when the hub 101 is mounted on the axle tube 47, the annular shouldered portion 102, with the rim 46 and cross wall 43 define an encased chamber in which the outer wall surface of the hub, portion 102 is opposed to the inner wall surface of the rim 46, and the hub shoulder of the portion 102 is opposed to the cross wall 43. Also as shown in Figs. 2 and 4, the shoulder portion defines an annular recess 114 paralleling, and intermediate the outer and inner wall surfaces of the hub. The outer edge of this recess defines a plurality of peripherally spaced slots 115, extending through the face of the shoulder, and a plurality of passageways 116, defined in the hub 101, communicate between the bottom of the recess and the interior of the nozzle structure within the hub, and at the roots of the nozzles 103 and 104.

Within the recess 114 is disposed an annular seal member 117 of a resilient, deformable material, such as an O ring of rubber or a synthetic material. Also disposed in the recess 114 toward the outer end thereof is an annular overriding clutch plate 118 provided with a plurality of ear portions 118a adapted to fit the slots 115 in the face of shouldered portion 102, and equal in number to the number of such slots. Each ear portion 118a is under cut to permit a portion of the plate to enter the recess below the bottom of the slots, and to provide clearance for reciprocal movement o'f the ears and plate within the depth of the slots.

As" shown more specifically in Fig. 5, the outer face of the clutch plate 118 is provided with a series of tooth and notch portions 119 and 120 respectively disposed in alternate sequence circtunferentially of the plate face. Each notch has a depth substantially equal to the height of adjoining tooth portions, and the tooth wall or face connecting between the crown of a tooth and the bottom of a notch is angled toward the notch center. Preferably the tooth face angle is from about 30 to about 60 to the clearance line. The total depth of each tooth and each notch is preferably substantially equal to the depth of the plate under cut portion, and the total thickness of the plate, including the tooth portions, is substantially equal to the depth 'o'f'thjeslots 115.

Next in sequence from the face of shoulder portion. 102 toward the inner end of the hub 101, is an annulargear 121, having peripheral gear teeth matched to the spur gear pinion 29, and adapted to be disposed forrotation on the hub while engaged by said spur gear. The outer face of the gear 121 provides a series of'notch and tooth portions 122 and 123 respectively, similar and' equal in number to those provided by the plate 118, butface of the gear, which butts against the shoulder facej portion. The gear is retained against the shoulder face, by a spring steel retainer ring 124 fitting against the face of a recessed portion on the inner side or face of the gear and engaged at its inner periphery in an annular groove in the wall of thehub portion 102.

In assembling the apparatus according to the present invention, a particular feature of the invention is emphasized. This feature involves the separability and re:

placeability of the gear reduction drive sub-assembly comprising the gear case 1.

This unit provides the first unit in the assembly-procedure, and is preferably placed on a flat-surface, or held in a vise, with the extended end of shaft 20 and-the boss 14 uppermost. The shaft 2% is then rotated, as by means of a screwdriver blade in the slotted portion 20d, so as to align the slot in substantially parallel relation to the axis of the shaft 25. With the shaft 20 in this position, the impeller case 2 is prepared for mounting on the gear case 1 by rotating the shaft 54 with means of a screwdriver blade inserted in the slot 540, so as substantially to align the tongue 54a with the axis of the dilfuse'r element 4&5 and axle tube 47. With the shafts thus positioned, the impeller case flange 2a is applied to the bosses 15 at the forward portion of the side wall 11 and substantially at the ends of the gear case cross wall 12, and slid over the remaining bosses 15 to the outer periphery of the boss 14. During such movement, the recessed portion 64 will first engage the vertical walls of the shouldered portions 16a and 17a, in the bosses 16 and 17 respectively, thereby to be guided for alignment of the impeller shaft tongue 54a, with the slot 20d in the shaft 2%. When the recessed portion 64 abuts against the wall of shoulder 18, the impeller case will be positioned with the spur gear 29 in thechamber provided therefor in the portion 46a, and with the shaftway in the portion 42a substantially centered on the threaded end of the shaft 31. As thus'positioned, the flange 2a is bolted to the bosses 15 and 14.

Next, the tube '71 is applied over the tubular inlet portion 44a, the shoulder 73 engaging the rim 52b of the attached guide vane element. With the tube 71 in place, the housing cap 51 is applied over the tube so as to align the peripheral and extended boss portions of the cap, such as designated by the numerals 86 and 37, with the corresponding bolt holes in the flange 2b of the'impeller case 2. By reason of the predetermined location of the radial extension 3%, this part is now located so as to aiign its defined shaftway 33a with the shaftway 42b defined in the portion 42a of impeller case 2. Before mounting the housing cap 81, of course, the seals Si? and $2 have been properly applied in their receiving groove portions shown, and the ring gear 76 andbearing parts 77 and 73 have also been applied in the relationships shown and described. 7

Now the shaft 62 is inserted in the shaftway 83a, and

through that part 42b which is defined in the portion 42a of the impeller case 42, into threaded engagement with the upper end of the shaft 31 in gear case 1. Engage merit of the shafts 62 and 31 is accomplished by means of a screwdriver, of which the blade is-inserted in the slot portion 620. As the shaft 62 is thus engaged, theg'fiar 63'becomes engaged with the-gear 76. CQntinued'rotation of the shaft 62 rotates the tube 71, until the shaft is completely seated. The threaded cap 89 is then inserted to seal the chamber 88b.

The collar 91 is now slip fitted over the upper end of the tube 71 which extends through the upper end of the housing cap 81. The annulus 96 is then threaded on the tube with the internal annulus flange engaging a shoulder on the tube as shown, and the retainer ring 97 is applied. As previously noted, with the collar 91 at rest on the upper end of the cap 81, the crowns of the teeth 94 formed in the collar flange 91a should be in substantially co-planar relation to the crowns of the teeth 99 on the .lower end of the annulus 96. The male coupling 92 is now slip fitted over the end of the tube 71, and bolted to the collar 91, to complete the main part of the assembly.

- At this time, the nozzle stiucture may be prepared for mounting on the axle tube 47. As a first step, the seals 106, 107, 110, and 111 may be positioned in the receiving grooves therefor. Next the ring 117 is inserted in the recess 114, and the clutch plate 118 inserted over the ring 117 with the ears 118a disposed in the slots 115 and teeth 119 facing toward the inner end of the hub. The annular gear 121 is then applied, to the shouldered hub portion 102 with the teeth 122 facing the teeth 119 on plate 118, and the retainer ring 124 is fitted into the groove provided on the wall of shouldered portion 102.

-As thus assembled, the nozzle structure 4 is prepared for mounting on the axle tube 47. This is done by aligning the peripheral teeth on the gear 121 with the teeth on the gear 29, and sliding the hub 101 over the axle tube 47, with the threaded end of the stub shaft 49 extended through the hub axial passageway 10112. The cap 105 isthen threaded on the shaft 49, and the set screws 105a tightened. .,-A particular feature of the apparatus provided by the unitized assembly described resides in the arrangements whereby the operating parts required to be lubricated ardprotected from access of a cleaning liquid passed through the discharge passageway and nozzles. As shown, each compartment of the assembly except the nozzle structure is a substantially self contained unit, and, in the assembly is substantially separated from a next adjoining unit. Thus, with cleaning liquid employed at high pressures, the unit separation is utilized to prevent leakage from one unit from reaching another unit directly under the operating pressure. For example, a vulnerable area in most machines of the type contemplated is at the juncture between'the liquid inlet and the impeller housing, another is at the juncture between the gear enclosure andthe impeller housing and liquid flow passageway. In the apparatus according to the present invention each .of .these junctures are pressure relieved by direct access to an ambient atmosphere at a lower pressure. Thus, .the failure of the seals provided for high pressure zones does not automatically lead to contamination or damage in all adjoining zones. ,This feature is of special importance for the protection of such elements of the structure as the bearings and gears in the housing cap unit, the gear case unit, and the directly related nozzle drive.

Another particular feature of the apparatus is found in the provision for removal, replacement, or substitution of the drive gear sub-assembly as a unit. This may be accomplished by first rotating the collar and coupling 91 and 92 respectively to expose the cap 89 in extension portion 88, and then removing the cap to provide access to the upper end of the shaft section 62. With a screwdriver blade inserted in the slot 620, the shaft is unthreaded from its connection in the upper end of shaft 31, and lifted slightly in its shaftway to clear the boss 14. Then the tongue 54a in the upper end of the impeller shaft 54 is aligned in right angular relation to the cross wall 43 by turning the slot 540 in shaft 54 into such alignment. Now by sliding the assembled units 2, 3 and itforward over the bosses and 14, these units may be separated from the gear case unit 1. A new or replace ment gear case unit may be installed by reversing the procedure. By substituting gear case units having gear trains of different ratios, the operating characteristics of the assembly may be altered so as to provide for a wide range of rotational cycle rates for either or both of the nozzle structure and the complete assembly. It is preferred, however, that while rotational speeds may be altered the basic ratios between the rotation rate of the nozzle structure and that of the whole assembly be retained.

An additional feature of the invention is to be found in the simplified forms of the clutch mechanisms provided to permit manual rotation of the assembly about its longitudinal axis and of the nozzle structure about its rotational axis, without dismounting parts, and Without damaging effects upon gears, shafts and bearings included in the drive transmission system. In the one instance the clutch arrangement is such as to be engaged by the suspended weight of the assembly, plus the pressure of the cleaning liquid stream, in the other arrangement the clutch is engageable under the hydraulic pressure of the cleaning liquid stream as discharged from the nozzle structure.

In a typical cleaning operation, the assembly is prepared for use by connection to the discharge end of a high pressure hose or other conduit through the male coupling element 92. Usually such connection will be made with the assembly in a horizontal or vertical position, whereby the clutch teeth 94 and notches 93 of the collar 91 are disengageable from the notches 98 and teeth 99 of the annulus 96. With the connection made, the assembly is inserted through any suitable opening or hatchway in the top wall of a container vessel, and preferably a hatchway disposed in, more or less concentric relation with the walls to be cleaned or treated. This opening, because of the overriding clutch on the nozzle structure, need be only slightly larger than the greatest horizontal distance between the nozzle cap 105 and the toe portion of the gear case side wall 11. Should the nozzles be extended toward the sides of the assembly, they may be rotated manually, through the nozzle structure overriding clutch, so as to align them in substantially parallel relation to the longitudinal axis of the assembly. Although the supply hose or conduit usually will be sufiicient to support the weight of the machine, it is preferable to provide an auxiliary support means by attaching a rope to the collar ring 91b. This rope may also serve as a means for guiding the machine during introduction or removal of the machine.

When inserted Within the tank and suspended therein, a cleaning or treating liquid is supplied through the supply co-nduit connection under a pressure such as to discharge jetted streams thereof from the nozzles 103 and 104. Preferably the machine is located so as to be not more than about twenty feet from a major portion of the container vessel interior wall surfaces. If greater distances are involved, the machine may have to be relocated in different areas of the vessel to accomplish proper contact of the jetted streams with all portions of the wall surfaces. Flow straightening means formed and/ or disposed in the discharge nozzles will aid in delivery of solid streams of liquid for impact against the wall surfaces to be contacted thereby.

The liquid flowing through the inlet tube 71 is directed against the impeller blades 57 by means of the vanes 53, both at the inlet of the passageway 41 defined in the impeller case 2. Thence flow passes outwardly through the axle tube 47, and is discharged over the diffuser element 48 through the nozzles 103 and 104. In passage through the nozzle structure 4, the pressure of the liquid flow stream is applied through the passages 116 and recess 114 to the inner side of the 0 ring 114a, forcing the ring toward the outer end of the recess and into engage: ment with the clutch plate 118. Under such pressure,

aelzaaa the Q ring and plate 118 are moved toward the toothed outer face of the gear 121, which is held against movement inwardly of the assembly by means of the retainer ring 124. In this first engaging relationship, the teeth. and notches in the plate 118 and. gear 121 may or may not mesh.

In the meantime, however, action of the flow stream on impeller blades 57 will rotate the shaft section 54 and in turn the shaft section in case 1 to actuate the gear train and shaft 25. Through shaft and spur pinion 29' and the annular gear 121 is rotated, and as the tooth and notch portions of the plate 118, and gear 121 come into meshing relationship, the pressure on the 0 ring 11441 forces plate 118 into meshed engagement with the gear 121. Rotation of the plate by engagement with the gear is transmitted to the nozzle structure through the ears and slots 118a and 115 respectively. So long as pressure is applied to the 0 ring the gear will be main-.- tained in locked driving relation to the nozzle hub. When the liquid pressure on the O ring 114a is relieved, the clutch plate and gear faces do not disengage automatically, but when the nozzle is rotated manually, the plate 118 will be forced into the recess as the teeth 119 ride over the angled wall portions of the teeth 123, along with the O ring 114a.

Actuation of the gear train and the shaft 25 also will actuate the shaft section 31, and through it the shaft section 62. As previously described, the gear 76 is fixed in relation to the tube 71 by the tooth and recess portions 74a and 76a respectively. Also, the tube 71 is rigidly fixed by the weight of the assembly and the water pressure to the coupling 92 through the overriding clutch arrangement, the toothed collar and annulus members, and through the coupling to the connected supply conduit means. Rotation of the shaft 62 and the attached gear 63, therefore, causes the gear 63 to walk around the fixed gear 76 as a satellite while drawing the assembled portions including cases 1 and 2, and housing cap 81 along, with consequent rotation of the assembly about the tube 71 and the longitudinal axis. In the meantime, of course, the nozzle structure is rotated about the axle hub.

Each of the spur pinions 28 and 29 being driven through the same shaft 25, and at the same speed, if bothv gears 76 and 121 had the same number of teeth, nozzle and assembly would rotate at the same rate, and the paths of the nozzle discharge streams would be constant and would track. The object, however, is to provide .constantly changing stream paths within the limits of eflicient operation. It has been found that with a liquid pressure of between about 150 to about 200 pounds, sufficient impact force is obtained at a distance of about twenty feet to produce effective scouring dispersion of the streams, at the impact surface, and to obtain effective cleaning action, if the stream paths are separated by about one foot. This result is obtainable in sixty-three revolutions of the entire assembly if the gear 76 has sixty-four teeth and the gear 121 has sixty-three teeth.

With such a proportional relationship, for each revolution of the complete assembly about the longitudinal axis, the nozzle will make about 1.0158 revolutions about,

the radial axis provided by the axle tube 47. In other words, for every completed revolution of the assembly about the sixty-four tooth gear 76, the nozzle will make one revolution about the tube 47, plus a distance equivalent to one more tooth, since the gear 121 has only sixtythree teeth. The difference as noted above is .0158 revolution, or 5.71 (360+63) in the 360 periphery of each of the gears 76 and 121.

With the axis of the nozzle considered to be located in a horizontal plane the axis of each stream will describe a curved path the tangent .of which is 45 in relation to such plane, and will advance about 5 .7l along a circle in the stated reference plane, in each revolution of the assembly. With two nozzles as shown, the respective paths will be separated by 2.855". Also, inasmuch as two nozzles are employed, in any series of successive travel paths, one will be in a downward direction and one in an upward direction. All paths in the same direction will be parallel, and with those extending generally upward intersecting those extending generally downward substantially to form a criss-cross or checkerboard pattern over any given wall surface.

The path relationships preferred have been stated, others may be attained by varying thehunting tooth ratio, i.e., a tooth relationship of 62 to 64 between the nozzle and assembly gears 121 and 76 respectively would result in a different degree advance of eachpath, namely 5.8064" (360+62). If the ratio were 65 teeth in the nozzle gear to 64 in the assembly gear, the advance would be 5.6923. After one cycle, or a number of revolutions about the longitudinal axis of the assembly which is equal to the number of teeth in the nozzle gear 121, the paths repeat themselves. As may be noted, the degree of advance decreases With an increase in the number of teeth in the nozzle gear 121, and the number of paths described increases.

The rate at which the cycle is accomplished depends entirely upon the reduction accomplished by the gear train within the gear case 1. In a preferred system as shown, the ratio between the Worm 19 and the wheel 21 is 40:1, and between the pinion 23 and spur gear 24 it is 53:12. The ratios between the gears 121 and 76, and the pinions 29 and 63 are 63:10 and 64:10 respectively. Where intensive contact action is required, the reduction is increased and thereby the speed of rotation is reduced, enabling the streams to pass over the wall surfaces more slowly. In a similar instance, if the number of teeth the nozzle gear 121 is increased separation of the successive paths over the surface would be reduced. Ordinarily, the ratio between nozzle gear 121 and assembly gear '76 is preferred to be 63:64. More intensive or less intensive contact is attained by varying the speed, or gear reduction ratios in the case 1. To accomplish such speed variations, any one of a series of gear trains may be substituted by substituting units containing such pre selected trains in the manner previously described. 'If more than two nozzles are employed in the nozzle structure, the pattern described will not change substantially, but the forming paths will be closer together.

In the alternate apparatus form illustrated by Fig. 6, an overriding clutch mechanism, substantially corresponding to that disposed at the upper end of the tube 71 in Fig. '3, is contained internally of the housing cap portion of the unit 3 of the complete assembly. The parts of the alternate construction form corresponding to similar parts in the other drawings are designated by similar numerals, but in the series.

The numeral 171 then designates a support tube having a shoulder 174 on which have been formed a series of circumferentially spaced upstanding tooth elements 194 with notch portions between the teeth. A ring gear 176, adapted for engagement with a drive pinion 163, is disposed over the tube 171. The lower face of the gear 176 is also provided with tooth and notch portions adapted to match those in the face of shoulder 174. The numeral 199 designates one such tooth. Except when the tooth and notch portions of the gear are engaged with similar portions in the tube shoulder face, the gear and tube are rotatable with reference to one another.

Also mounted on the tube 171 is one part of a roller bearing, which part includes a raceway 177 and rollers 177a. The raceway is disposed for relatively free reciprocal movement on the tube. A housing cap 181 fits over the tube 171 as shown, and contains theother raceway 178 of the roller bearing assembly.

The outer or upper end of tube 171, which extends beyond the cap 181 is adapted for fixed threaded en,- gagement by a male coupling element 192. A set screw 192a holds the element against rotation after assem- 1 bly. The lower end of the coupling 192 is disposed so that the tube shall be free to move reciprocally with respect to the cap 181 for adistance at least equal to the least height of either series of teeth 194 or 199.

In use, when the tube is relieved of the weight of the assembly it will tend to move downwardly through the housing cap 181. In this condition, rotation of the tube 171 or gear 176, one relative to the other will cause the gear teeth 199 to ride over the tube shoulder teeth 194. When the assembly welght and water pressure is transmitted to the tube 171, the gear 176 will be forced against the bearing raceway 177, and the raceway in turn against a shoulder 171a in the tube 171. In this position the teeth 194 will be unable to override the teeth 199, and therefore, the gear will be rigidly related to the tube, whereby rotation of the pinion 163 will causethe rest of the assembly to be rotated about the tube.

What is claimed is:

1. In apparatus of the character described, including a support tube defining a liquid conduit having inner and outer ends, a housing assembly supported coaxially from said tube inner end for rotation about said tube axis in substantially fluid tight relation to said tube, wherein said housing assembly includes an impellercase defining a liquid passageway opening from said tube subport at one end through an annular support axle extended radially from said case at the other end, and a nozzle structure mounted on said axle in rotatable coaxial relation thereto, a means for rotating said nozzle structure about its axis comprising a hub on said nozzle structure adapted for telescopic rotatable engagement on said axle, a shouldered portion on said hub defining a radial face and a circular longitudinal wall at right angles to said face, an annular gear mounted and retained on said shoulder wall, freely rotatable thereon, said gear having an inner face disposed in opposed relation to said shoulder face, a plurality of tooth and notch portions on said gear inner face, an annular recess defined in said shoulder face, a plurality of passageways defined in said hub to extend and communicate between said recess and the interior of said nozzle structure, a resilient deformable seal ring fitted in said shoulder face recess for reciprocally displaced movement therein, an annular clutch plate mounted for reciprocal movement on said hub shoulder wall and intermediate said seal and said gear, said plate engageable therebetween, said plate having an outer face disposed in opposed'relation to said inner gear face, a plurality of tooth and notch portions on said plate outer face adapted to mesh with those on said gear inner face, and means to retain said clutch plate against rotation on said hub shoulder wall.

2. An apparatus for applying liquid streams to the interior wall surfaces of a container vessel, comprising in combination a suspension and support tube having inner and outer ends, coupling means at the outer end of said tube mounted for rigid attachment of said tube to a 'liquid supply conduit, an enlarged portion at the inner end of said tube forming interiorly and exteriorly disposed shoulders respectively facing toward said inner and outer tube ends,'a first ring gear mounted on said exterior shoulder, in fixed relation thereto, a housing rotatably mounted on said tube comprising an annular housing cap concentric with said tube and disposed for rotative support thereby in fluid-tight relation thereto, an impeller case supported by said cap in dependent spaced relation thereto, said case including a top wall defining an upstanding tubular conduit portion adapted to engage said tube within the enlarged lower end thereof for fluid tight rotative relation thereto, front wall and bottom wall portions integral with said case, a tubular nozzle axle mounted on said front wall and disposed in right angular relation to the axis of said tube,.a passagethrough said axle, an impeller shaft and impeller mount-- ed in said passageway in axial relation to said tube, said shaft extending through the bottom wall of said case, a nozzle structure having a hub mounted on said axle for rotation thereon, overriding clutch means mounted on said hub, said means including a second ring gear rotatable on said hub, hydraulic means mounted on said hub to engage said clutch means between said gear and nozzle hub, a gear case sub-assembly unit, having top, front and side wall portions, said gear case top wall portion being separably attached to said impeller case bottom wall in axially spaced dependent relation thereto, a drive shaft extending from said gear case and disposed for relation axially to said impeller shaft including separable connective means therebetween, a separable drive connection between said gear case and said first ring gear, and a separable drive connection between said gear case and said second ring gear.

3. An apparatus according to claim 2 wherein said coupling means comprises an annulus retained in fixed threaded engagement on said tube, said annulus having a toothed lower end, wherein said teeth include angularly inclined side wall portions, an annular coupling element and collar combination enclosing said annulus, said collar having an inwardly flanged shouldered portion toothed about its upper. surface in matching relation to the lower toothed end of said annulus, said collar and coupling combination disposed for reciprocal movement longitudinally of said tube for a distance at least equal to the distance between the root and face of one said tooth portion.

4. In an apparatus of the character described, including a support tube defining a liquid conduit having inner and outer ends, an enlarged portion at the inner end of said tube forming. exteriorly disposed annular shoulders facing toward said tube outer end, and a housing assembly supported coaxially from said tube shoulders by means of an annular cap fitted to said tube in telescopic, substantially fluid tight relation, for rotation about said tube axis and for limited reciprocal movement longitudinally thereof, saidcap and tube defining a sealed chamber including said tube shoulders as wall portions thereof; a means for rotating said assembly about said tube comprising a ring gear disposed in said chamber, encompassing said tube, said gear having a lower face opposed to one said tube shoulder, a circumferential matching'series of tooth and notch portions on each said shoulder and said ring gear lower face engaged and disengaged by reciprocal movement of said assembly relative to said tube; a shaft way defined in said assembly in axially parallel relation to said tube; a drive shaft in said shaftway, and a pinion gear carried by said shaft for meshed relation with said ring gear.

5. An apparatus according to claim 1, wherein said means to retain said clutch portion against rotation on said hub shoulder wall comprises a series of slots defined in said shoulder face in circumferentially spaced relation radially of said face, and a corresponding series of radial ear portions on'said clutch plate, adapted for engagement in said slots, said ear portions having a thickness less than the depth of said slots and said plate having a thickness substantially equal thereto.

References Cited in the file of this patent UNITED STATES PATENTS

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