US3584790A - Oil tank washing machine - Google Patents

Abstract

The machine for washing the interior surface of a hollow structure includes a head assembly mounted for rotation about a first axis. A wash fluid discharge head is mounted on head assembly for rotation with respect thereto about a second axis at an angle to said first axis. The head assembly has a passage for receiving and transferring wash fluid to the wash fluid discharge head. A wash fluid actuated rotary drive means is mounted on the head assembly externally of the passage. A fluid feed passage extends from the first passage to the drive means. Transmission means is connected to the drive means to effect simultaneous rotational movement of the head assembly about the first axis and the wash fluid discharge head about the second axis. The transmission means includes means for effecting intermittent accelerations or decelerations in the rotational speed of the wash fluid discharge head relative to the rotational speed of the head assembly.

Description

United States Patent Inventor Robert Benham Bonfield Goring-by-Sea, England Appl. No. 788,421 Filed Jan. 2, 1969 Patented June 15, 1971 Assignee Dasic Equipment Limited Southampton, England Priority Jan. 9, 1968 Great Britain 1264/68 OIL TANK WASHING MACHINE 12 Claims, 8 Drawing Figs.

Primary Examiner- Lloyd L. King AttorneyAlexander & Dowel] ABSTRACT: The machine for washing the interior surface of a hollow structure includes a head assembly mounted for rotation about a first axis. A wash fluid discharge head is mounted on head assembly for rotation with respect thereto about a second axis at an angle to said first axis. The head assembly has a passage for receiving and transferring wash fluid to the wash fluid discharge head. A wash fluid actuated rotary drive means is mounted on 'the head assembly externally of the passage. A fluid feed passage extends from the first passage to the drive means. Transmission means is connected to the drive means to effect simultaneous rotational movement of the head assembly about the first axis and the wash fluid discharge head about the second axis. The transmission means includes means for effecting intermittent accelerations or decelerations in the rotational speed of the wash fluid discharge head relative to the rotational speed of the head assembly.

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WWW W OIL TANK WASHING MACHINE DESCRIPTION OF THE INVENTION The invention relates to machines for washing the interior surfaces of hollow structures, and particularly to machines for washing the interiors of the tanks of marine oil tanks with high pressure fluid jets.

The invention provides a machine for washing the interior surface of a hollow structure comprising a head assembly, means for mounting the head assembly for rotation about a first axis, a wash fluid discharge head mounted on said head assembly for rotation with respect thereto about a second axis at an angle to said first axis, a passage in said head assembly for receiving and transferring wash fluid to said wash fluid discharge head, wash fluid actuated rotary drive means mounted on said headassembly externally of said passage, a fluid feed passage extending from said passage to said drive means, and transmission means connected to said drive means to effect simultaneous rotational movement of said head assembly about said first axis and said wash fluid discharge head about said second axis, said transmission means including means for effecting intermittent accelerations or decelerations in the rotational speed of said wash fluid discharge head relative to the rotational speed of said head assembly.

In consequence of the accelerations or decelerations, jets of wash fluid from said wash fluid discharge head are precessed slightly at each passage around the interior surface of the hollow structure washed by the machine so that the whole of said interior surface can be effectively washed.

The invention may further comprise the features hereinafter described with reference to the accompanying drawing in which:

FIG. 1 is a perspective view of a machine according to the invention,

FIG. 2 is a sectional side elevation on the line II-II of FIG. 1,

FIG. 3 is a sectional plan view on the line IIlIII of FIG. 2,

FIG. 4 is a sectional side elevation on the line IV-IV of FIG.

FIG. 5 is a sectional side elevation of a modified embodi-. ment of the invention, the Pelton wheel and transmission system being omitted from the drawing in order to illustrate the modifications with greater clarity,

FIG. 6 is a sectional side elevation of a further modified embodiment of the invention,

FIG. 7 is a sectional plan view on the line VII-VII of FIG. 6, and

FIG. 8 is a sectional plan view on the line-VlIl-VIII of FIG. 6.

Referring first to FIG. 1, the machine comprises a wash head body portion 1 having a washfluid discharge head 2 mounted thereon for rotation about a horizontal axis. Thedischarge head 2 comprises two oppositely directed nozzles 3. The body portion 1 is mounted for rotation at the lower end of a wash fluid supply tube 4 terminating in a flange 5.

Referring now to FIG. 2 to 4, the machine comprises astub pipe 6 having aflange 6a at the upper end thereof for facilitating bolted connection to the flange 5 of the supply tube 4. At its lower end, thestub pipe 6 is provided internally witha spider 7 from which depends astatic shaft 8 coaxial with thestub pipe 6.

Between theflange 6a and the spider 7, thestub pipe 6 carries a graduatedfilter structure 6b. The comprises a series of spaced gauges, the mesh sizes of which decrease in a direction from theflange 6a towards the spider 7.

The body portion 1 comprises aneck portion 9 dimensioned for rotation on the lower end thestub pipe 6 and provided with a labyrinth gland I0. The body portion-I is divided into two chambers by an internal wall, namely awash fluid chamber 12 and a precess anddrive gear chamber 13. Theshaft 8 extends through a gland structure 14 in the wall which is vented from a central position by a vent l5.

Thechamber 12 is defined in part by theneck portion 9 and comprises aninclined passage 16 which terminates in ahorizontal bore 17. At the inner end of thebore 17, a smallconcentric bore 18 is provided into thechamber 13. Journaled for rotation in thebores 17 and 18 respectively are a hollowcylindrical body 19, forming part of thedischarge head 2, and astub shaft 20 extending therefrom, thebores 17 and 18 being provided withlabyrinth glands 21 and 22, and O-ring seals at 2111.

The end of thestub shaft 20 extending into thechamber 13 has abevel crown wheel 23 keyed thereon and retained by a nut.

Thecylindrical body 19 has aninner end wall 25, anouter end wall 26 anapertures 24 in the cylindrical wall thereof which apertures 24 sweep across the end of thepassageway 16 during rotation of thecylindrical body 19. At its outer end, thecylindrical body 19 extends beyond the body portion 1 and carries the two nozzles 3 which extend in diametrically opposite directions. If desired the nozzles may be slightly offset on opposite sides of the diametric centerline of thecylindrical body 19 so as to provide an assisting torque during rotation of thedischarge head 2.

At its lower end, thestatic shaft 8 is journaled in a thrust bearing 27 set in alower cover 28 of the body portion 1 and adapted to transfer the full weight of the body portion 1 and dischargehead 2 machine onto theshaft 8. The thrust bearing 27 may comprise a ball race generally as shown in FIG. 2 or a dry lubricated bearing may be used, for example utilizing sintered bronze/polytetrafluoroethylene/lead bearing surfaces. Abearing cover 27a is provided to protect the bearing.

Aworm wheel 29 is secured by ashear pin 30 on theshaft 8 at a position within thechamber 13 just above the bearing 27. Theworm wheel 29 carries an upwardly extendingstepped sleeve bushing 31 on which is keyed aquadrant plate 32.

Mounted for rotation on theshaft 8 above thequadrant plate 32 is apinion 33 having an upwardly extending sleeve bushing 34 formed as abevel pinion 35 at its upper end, the bevel pinion 3S meshing with thecrown wheel 23 mounted on thestub shaft 20.

At a position spaced radially from theshaft 8, thequadrant plate 32 is bored to receive a sleeve bearing 36 in which aspindle 37 is journaled. At its lower end thespindle 37 carries apinion 39 which meshes with a pinion 40 (FIGS. 3 and 4). Thepinion 40 is mounted for rotation on aspindle 41 set in thequadrant plate 32 and is formed integrally at the lower surface thereof with astar wheel 42 having fourlobes 43.

Mounted in the body portion 1 in horizontal alignment with thestar wheel 42 is a strike pin 74 which extends inwardly to such a position that upon rotation the body portion 1 about thespindle 8 (as described below), the pin 74 strikes one of thelobes 43 and causes partial rotation of thestar wheel 42, this partial rotation being transmitted through thegears 40, 39, 38, 33, 35 and 23 to thehead 19, the overall reduction being 9:] to effect an acceleration of deceleration of thegear 35, thegear 23 and thus of the rotational speed of the wash fluid discharge head.

Theworm wheel 29 meshes with a worm 44 keyed to one end of ashaft 45. Apinion 46 keyed to the other end of theshaft 45 meshes with an idler pinion which in turn meshes with apinion 47 keyed to the end of a shaft 48. At the other end of the shaft 48 is keyed apinion 49 which meshes with apinion 50 keyed to adrive shaft 51. Theshaft 51 extends throughlabyrinth sleeve bearings 52 in the outer wall of the body portion 1 and has keyed to the other end thereof a Peltonwheel 53. Thebearings 52 are vented from a midposition by a vent 54.

The Peltonwheel 53 is enclosed in acover 55 bolted to the body portion 1. Thecover 55 carries apipe union 56 in one wall thereof to which anozzle 57 is secured for operation of the Pelton wheel. Apipe 58 extends from the other end of thepipe union 56 to asecond pipe union 59 mounted in the wall of thewash fluid chamber 12. Agauge filter 59a is provided as shown to prevent any particulate material from entering thepipe 59 that may have passed thefilter 6b.

Adischarge vent 60 is proved In thecover 55 for exhaust fluid from the Pelton wheel.

In operation, the machine is advantageously mounted as a permanent installation in a tank to be washed with theflange 6a being connected to the flange of the wash fluid supply pipe 4.

As soon as wash fluid under pressure enters thechamber 12 from the pipe 4, a small proportion is bled oflthrough thepipe union 59 andpipe 58 to thenozzle 57. The remainder of the wash fluid is fed down thepassage 16 and through theapertures 24 into thecylindrical body 19 where it is discharged through the nozzles 3. The fluid discharged through thenozzle 57 impinges on the buckets of thePelton wheel 53 to cause rotation thereof at a maximum speed of 2,600 r.p.m. and is then discharged through thevent 60 in thecover 55.

The rotation of the Pelton wheel is transmitted through thegear train 50, 49, 47 and 46 to the worm 44 so as to preferably provide a 100:] reduction from the speed of the Pelton wheel. Since thewonn wheel 29 is fixed by theshear pin 30 of theshaft 8, the rotation of the worm causes the body 1 to rotate about theshaft 8.

The initial rotation of the body 1 causes rotational movement to be imparted to thecrown wheel 23 due to its engagement with thelevel pinion 35.

A friction pad 320 is set into the lower side of thequadrant plate 32 so as to bear on thepinion 39 and prevent slip and consequent rotation of thegears 38 and 33 which would check this rotational movement. The pad 320 is loaded bysprings 32b set in bores in the quadrant plate and adjustable by grub screws.

As the body continues to move round theshaft 8, the striker pin 74, strikes one of thelobes 43 of thestar wheel 42 and causes, through thegear train 40, 39, 38, 33, 35 and 23 a momentary acceleration of thecylindrical body 19. The frequency with which this acceleration occurs can be varied by increasing or decreasing the number oflobes 43 on the star wheel and/or the number of striker pins 44 set in the body 1.

The striker pin 44 and/or thelobes 43 may also be longitudinally and/or radially adjustable respectively so as to regulate the frequency of striking and length of contact (and therefore extent of movement of the star wheel. The acceleration can also be varied by changing the gear ratios between thestar wheel 42 and thecrown wheel 23.

In a preferred embodiment, the body portion 1 rotates about thevertical shaft 8 at a speed of 5 revolutions per minute or less and the washfluid discharge head 2 rotates at a speed approximately one-third of but variable in respect of, the speed of the body portion 1.

The paths of impingement of the jets from the nozzles 3 on the walls of the tank are thus precessed slightly at each passage so that eventually the whole of the tank surface is washed.

Furthermore, by arranging the washfluid discharge head 2 to rotate more slowly than the body portion 1, the paths if impingement have a moderate slope and the jets are more effective in removing residues from horizontal surfaces in the tank.

The pinion andstar wheel 42 may be arranged for easy removal from the machine after removal of thecover 28 so that thestar wheel 42 or the gear train between the star wheel and thecrown wheel 23 may be changed to provide a ratio of rational speeds between the body portion 1 and the wash fluid discharge head to suit particular operating requirements.

In the embodiment described above, the number of teeth on the various gears were as follows.

In the modified embodiment of FIG. 5, the parts which are analogous to the construction of FIGS. 1 to 4 are given the same reference numerals, (the Pelton wheel, transmission and precess gearing being omitted for clarity).

This embodiment provides a modified body portion 1 and dischargehead 2 which incorporate a clutch and means wfi'etet' 'reatvitflartfi Panda's/Hearts ltrifitemany of the bod T: this end, thecrown wheel 23 is mounted on one end ofa shaft 61 by anut 62. The shaft 61 extends through thebore 18 and coaxially with thebore 17 in the body 1 to a position beyond the end of thebore 17. At its outer end, oneelement 63 of a core clutch is mounted on the shaft 61. At a position adjacent thebore 18, agland member 64 is keyed to the shaft 61, themember 64 incorporating a number of seals to prevent ingress of water to and through thebore 18.

Thewash head 2 is mounted towards the outer end of the shaft 61 for fee rotation thereon when the core clutch is disengaged between the coreclutch element 63 and the end of thebore 17. Thewash head 2 has two nozzles 3 extending radially therefrom and acylindrical boss portion 65 extending along thebore 17 as far as thepassage 16. At its outer face theboss portion 65 is formed with a coreclutch face 66 adapted to cooperate with theelement 63. The outer surface of theboss portion 65 is provided with aring seal 67 and sufficient clearance is provided between theclutch element 63 and the end of thebore 17 to permit limited axial sliding movement of thewash head 2 on the shaft 61.

At a position inwardly of theseal 67, theboss portion 65 is provided with an externalannular recess 68 into which a series of holes 68a vent from the interior of the boss. Theholes 68 also act as a strainer. Apassage 69 extends from the annular zone in which therecess 68 in the boss rotates and through the body 1. The other end of thepassage 69 connects with thenozzle member 57 mounted in the Pelton wheel compartment (not shown) for actuation of the Pelton wheel.

Thepassage 69 is preferably formed as an integral part of the body casting although an external pipe may be provided if required similar to thepipe 58 of FIG. 1.

Turning now to FIGS. 6 to 8 the embodiment shown comprises a washhead body portion 101 having a washfluid discharge head 102 mounted thereon for rotation about a horizontal axis therein. The wash fluid dischargedhead 102 having two oppositely directednozzles 103.

Thebody portion 101 comprises aflange 104 adapted to be bolted to a cooperating flange (not shown) provided on the end of a wash fluid supply pipe. Afirst element 105 of a clutch is secured on the underside of theflange 104 by set screws, the clutch face being formed by thelower surface 106 of an internalannular recess 107 formed therein. An O-ring seal 108 is also provided in theelement 105 above therecess 107.

The O-ring seal 108 is engaged by the upper end of anentry pipe 109 which also has an externalannular flange 110 engaging in therecess 107, thelower face 111 of theflange 110 forming the second clutch surface.

The entry pipe also has aspider 112 mounted internally therein, from which depends astatic shaft 113 coaxial with theentry pipe 109.

Aneck portion 114 of the body portion 1 is dimensioned for rotation on the lower end of theentry pipe 109, an O-ring seal 1 15 being provided between the two members.

The body portion 1 is divided by internal walls 1 16, 117 and 118 into awash fluid chamber 119, aprecess gear chamber 120, atransmission gear chamber 121 and aPelton wheel compartment 122, the chambers being generally arranged in sequence one beneath the other.

Thechamber 119 is defined in part by theentry pipe 109 and also comprises aninclined passage 123 which terminates in ahorizontal bore 124 At the inner end ofbore 124, a smallconcentric bore 125 is provided into thechamber 120. Journaled for rotation in thesmall bore 125 is ashaft 126 having abevel crown wheel 127 keyed to the end extending into the chamber and secured by a nut. The bore is provided with alabyrinth gland 128 around theshaft 126. Aflange member 129 keyed onto theshaft 126 adjacent thebore 125 and has an O-ring seal 130 which seals against acylindrical surface 131 forming part ofinternal wall 116. Thegland 128 and seal 130 prevent ingress of water through thebore 125 to thechamber 120.

Theshaft 126 extends beyond the end of thebore 124 and at its outer end carries oneelement 132 of a core clutch secured by a nut 1320. Thewash head 102 is mounted for free rotation on theshaft 126 when the clutch is disengaged between the coreclutch element 132 and the end of thebore 124. The wash head has acylindrical boss portion 133 extending into thebore 124 as far as thepassage 123. At its outer face thewash head 102 has a recess coaxial with theshaft 126,

the wall of the recess defining a coreclutch face 134 adapted to cooperate with theclutch element 132. The outer surface of theboss portion 133 is provided with an O-ring seal 135 and sufficient clearance is provided between theclutch element 132 and the end of thebore 124 to permit limited axial sliding movement of thewash head 102 on theshaft 126.

At a position inwardly of theseal 135, theboss portion 133 is provided with an externalannular recess 136 into which a series ofholes 137 vent from the interior of the boss. Theholes 137 also act as a strainer. Apassage 138 formed in thebody 101 extends form the annular zone in which therecess 136 in the boss rotates and terminates at theinternal wall 118. Aremovable nozzle member 139 is mounted in thePelton wheel compartment 122 and in communication with thepassage 138, by aset screw 140.

Thestatic shaft 113 extends downwardly through agland structure 141 incorporating two external and two internal 0-ring seals 142 and 143 respectively and which is vented from a central annular recess by avent 144. At its lower end, thestatic shaft 113 is journaled in a thrust bearing 145 set in the internal wall 117 and adapted to transfer the full weight of the machine onto theshaft 113. The thrust bearing 145 is enclosed by a cover plate 146 and may comprise a ball race generally as indicated in FIG. 6. Alternatively, a dry lubricated bearing may be used as described with reference to the embodiment of FIGS. 1 to 4.

A pinion 147 is keyed on theshaft 113 and secured by a nut 148 at a position within thechamber 120 immediately above the thrust bearing 145. The pinion 147 carries an upwardly extending steppedsleeve bushing 149 on which is keyed aquadrant plate 150. Mounted for rotation on theshaft 113 above the quadrant plate on a spacer washer (not shown), is aworm wheel 151 having an upwardly extendingsleeve bushing 152 formed as abevel pinion 153 at its upper end, thebevel pinion 153 meshes with thecrown wheel 127.

At a position spaced radially from the shaft (see FIG. 7), the quadrant plate carries two bearingbrackets 154 in which the spindle ofaworm 155 is journaled, the worm meshing with theworm wheel 151, At one end, the spindle of the worm extends through therespective bracket 154 and has apinion 156 keyed thereto. Thepinion 156 meshes with apinion 157 keyed on the end of aspindle 158, the spindle 148 being journaled in afurther bearing bracket 159 on thequadrant plate 150. The other end of the spindle 148 has a sixlobed star wheel 160 keyed thereto, thestar wheel 160 having its axis lying on an extended radius of theshaft 113.

Mounted in thebody portion 101, also on an extended radius of theshaft 113 but above the axis of thestar wheel 160, is astriker pin 161. Thestriker pin 161 is threaded at its outer end for adjustment and extends inwardly to such a position that upon rotation of thebody portion 101 about the shaft 113 (as described below) thepin 161 strikes one of the lobes of thestar wheel 160 to cause partial rotation of thestar wheel 160, the partial rotation being transmitted through thegears 157, 156, 155, 151, 153 and 127 to theshaft 126 and thewash head 102 to effect an acceleration or a deceleration of the rotational speed of thewash head 2. g

The pinion 147 meshes with asmaller pinion 162 keyed to the upper end of avertical shaft 163. Theshaft 16;} extends downwardly through asleeve bearing 164 in the inner wall 117, the bearing 164 incorporating inner andouter seals 165.

At its lower end, (See FIG. 6 and 8) in thetransmission gear chamber 121, theshaft 163 is provided with a socket 166 which envelops the end of ashaft 167 having aworm wheel 168 keyed thereto. A drive connection between the socket 166 and theshaft 167 is provided by ashear pin 169 extending transversely through both elements. The lower end of theshaft 167 is journaled in abearing 170 formed in thewall 118. A worm 171 (FIG. 8) meshes with theworm wheel 168 and is keyed to ashaft 172 of which one end is journaled in abearing 173 formed in the outer wall of thebody 101 and the other end extends through abearing block 174 mounted on thewall 118. Afurther worm wheel 175 is keyed to the other end of theshaft 172 and meshes with aworm 176. Theworm 176 is keyed to avertical shaft 177 which at its upper end is journaled in abearing 178 in abracket 179 bolted to thewall 118. Thetransmission gear chamber 121 is preferably packed with grease.

The lower end of theshaft 177 extends downwardly through abearing 180 in theinner wall 118 and into thePelton wheel compartment 122, where aPelton wheel 181 is keyed or splined on theshaft 177 and secured by anut 182.

The lower wall of thebody 101 is formed by adetachable cover 183 having adischarge port 184 for exhaust water from thePelton wheel 181.

The machine is assembled, as indicated in FIG, 6, in tiered sections secured together by setscrews 185. This arrangement enables a machine to be provided which whilst having an output sufficient to operational requirements, can be passed through the standard 12.5 inch (32 centimeter) access holes which are normally provided in the tanks of marine oil tankers.

The machine shown in FIG. 6 to 8 is advantageously secured by theflange 104 to the flange of a wash fluid supply pipe. At this stage, and during the lowering of the machine through the access hole, thewash head 102 is free to rotate with respect to its fixedclutch elements 132. This prevents damage to the internal gearing due to torque inadvertently or improperly applied to thewash head 2 and also permits orientation of thenozzles 103 to allow the wash head to pass through the access hole.

Similarly, before lowering into the tank and during positioning when in the tank, the clutch 106/111 allows rotation of thebody 101 relative to the wash water supply pipe which again prevents damage to the internal gearing.

In operation, and after proper location in the tank, as soon as wash fluid under pressure enters thechamber 119, it is directed down thepassage 123, through thebore 124 andboss 133, and out through thenozzles 103. The optimum water pressure is approximately 200 pounds per square inch (14,000 gm./cm. and at this pressure, the pressure loadings on the upwardly presented face of theinner wall 116 and the inner surfaces of thewash head 102 are sufficient to engage theclutches 106/111 and 132/134 and prevent relative rotation between the parts.

A proportion of the wash fluid entering theboss 133 is bled off radially through theholes 137 into the annularexternal recess 136 in the boss. This wash fluid is then led through thepassage 138 and discharged through thenozzle 139. The fluid discharged impinges on the buckets of the Pelton wheel to cause rotation thereof and is then discharged through theport 184 in thelower cover 183.

The rotation of the Pelton wheel is transmitted through thegear train 176, 175, 171 and 168 to thepinion 162 so as to preferably provide a speed reduction of approximately 100:1 from the Pelton wheel speed. Since the pinion 147 is keyed to thestatic shaft 113, thepinion 162 carries out a planetary motion with respect to the pinion 147 and thereby causes thebody 101 to rotate around theshaft 113.

The initial rotation of thebody 101 causes thecrown wheel 127 to rotate due to its engagement with thebevel pinion 153. Thebevel pinion 153 is prevented from rotation by the locking action of theworm 155 on theworm gear 151 when reverse drive is applied.

As thebody 101 continues to move around theshaft 113, the striker pin 161 (FIG. 7) strikes one of the lobes of thestar wheel 160, and causes, through thegears 157, 156, theworm 155, theworm wheel 151, and thebevel pinion 153, a momentary acceleration of thecrown wheel 127 together with theshaft 126 and thewash head 102. The frequency with which this acceleration occurs can be varied by increasing or decreasing the number of lobes on the star wheel and/or the number of striker pins set in the body I. The acceleration can also be varied by changing the gear ratios between thestar wheel 160 and thecrown wheel 127.

in consequence of the momentary acceleration, the jets from thenozzles 103 are precessed slightly at each passage round the walls of the tank so that the whole zone of the tank surface covered by the machine is eventually washed.

In all of the embodiments above described, the wash fluid discharge head is preferably arranged to rotate at a speed (neglecting the momentary accelerations) slower than that of the body portion 1. The paths of impingement of the jets are then more effective in removing residues from horizontal surfaces in the tank.

In one machine having a jet range of approximately 120 feet (37 meters) thebody 101 rotates about the vertical axis on theshaft 126 at 1.5 revolutions per minute whilst the washfluid discharge head 2 rotates about the horizontal axis of theshaft 126 at 0.5 revolutions per minute. in a smaller machine having a jet range of approximately 55 feet (17 meters) thebody 101 rotates at 3 revolutions per minute whilst the washfluid discharge head 2 rotates at l revolution per minute.

I claim:

1. A machine for washing the interior surface of a hollow structure comprising a head assembly, means for mounting the head assembly for rotation about a first axis, a wash fluid discharge head mounted on said head assembly for rotation with respect thereto about a second axis at an angle to said first axis, a passage in said head assembly for receiving and transfering wash fluid to said wash fluid discharge head, wash fluid actuated rotary drive means mounted on said head assembly externally of said passage, a fluid feed passage extending from said first passage to said drive means, and transmission means connected to said drive means to effect simultaneous rotational movement of said head assembly about said first axis, and said wash fluid discharge head about said second axis, said transmission means including means for effecting intermittent accelerations or decelerations in the rotational speed of said wash fluid discharge head relative to the rotational speed of said head assembly.

2. A machine as claimed in claim 1, wherein said transmission means comprise a static shaft, a first gear mounted for rotation on said shaft, a second gear mounted for driving said wash fluid discharge head and meshing with said first gear, a third gear secured on said shaft, reduction gear means connecting said drive means to said third gear for causing rotation of said head assembly around said shaft, means resisting rotation of said first gear by said second gear so that said second gear is driven inconsequence of the rotation of said head as sembly, a rotary lobed element connected for driving said first gear, and striker means mounted in said head assembly for repeated engagement with said lobed element during rotation of the assembly whereby intermittent accelerations or decelerations of said first and second gears are effected.

3. A machine as claimed inclaim 2, wherein the means re sisting the rotation of the first gear comprises a friction clutch.

4. A machine as claimed inclaim 2, wherein the means resisting the rotation of the first gear comprises a worm meshed ll!!! awmlhsslm q for tetiti s it .thsfie! gear 5. A machine as claimed in claim 4, wherein the worm is mounted on a spindle connected through a gear train to a further spindle carrying said lobed element, said further spindle being disposed radially with respect to said static shaft.

6. A machine as claimed inclaim 2 in which the means mounting the head assembly for rotation comprises a pipe having a flange at one end adapted to bolted to a flange of a wash fluid supply pipe, said pipe comprising at its other end an internal support member to which the upper end of said static shaft is coaxially secured, said other end being received within a tubular inlet portion of said head assembly.

7. A machine as claimed inclaim 6, wherein said pipe is divided into two annular portions and wherein said annular portions are connected by a friction clutch.

8. A machine for washing the interior surface of a hollow structure, comprising, in combination, a head assembly having a body member having an inlet passage, an outlet passage defining a bore a passage interconnecting said inlet and outlet passages, a first inner wall dividing said passages from a gear chamber, a second inner wall dividing said gear chamber from a Pelton wheel compartment having an exhaust part therein, an inlet pipe received at one end in said inlet chamber for rotation of said body with respect thereto, a flange on the other end of said inlet pipe for secural to a flange of a wash fluid supply pipe, a thrust bearing located at a transverse wall of said body member beneath said first inner wall, a sealing gland mounted in said first inner wall in axial alignment with said, thrust bearing, a static shaft carrying at its lower end the weight of said body through said thrust bearing and extending upwardly through said sealing gland, means supporting the upper end of said shaft coaxially in said inlet pipe, a first gear mounted for rotation on said static shaft a second gear meshing with said first gear and operatively connected through sealing means in said first inner wall with a wash fluid discharge head mounted for rotation in said outlet bore, a third gear secured on said static shaft, a Pelton wheel mounted for rotation in said Pelton Wheel compartment, reduction gear means connecting said Pelton wheel to said third gear for causing rotation of said head assembly around said shaft means resisting rotation of the first gear by said second gear, so that said second gear is driven in consequence of the rotation of said head assembly, a rotary lobed element connected for driving said first gear, striker means mounted in said head assembly for repeated engagement with said lobed element whereby intermittent accelerations or decelerations of said first and second gears are effected, and means defining a fluid feed passage extending between one of said first mentioned passages and said Pelton Wheel compartment and terminating in a nozzle or nozzles disposed for directing impulse jets at the buckets of the wheel.

9. A machine as claimed inclaim 8, wherein the means resisting the rotation of the first gear comprises a friction clutch.

10. A machine as claimed inclaim 8, wherein the means for resisting the rotation of the first gear comprises a worm meshed with a worm wheel mounted for rotation with the first gear.

11. A machine as claimed inclaim 8, wherein said Pelton wheel compartment is mounted at the lower end of the head assembly and wherein the third gear is driven by a pinion connected to said Pelton wheel through a two stage worm and wheel reduction gear train located in a compartment intermediate said transverse wall and second inner wall.

12. A machine as claimed inclaim 8, wherein said wash fluid discharge head is connected to said second gear through means comprisiga friction clutch.

Claims (12)

1. A machine for washing the interior surface of a hollow structure comprising a head assembly, means for mounting the head assembly for rotation about a first axis, a wash fluid discharge head mounted on said head assembly for rotation with respect thereto about a second axis at an angle to said first axis, a passage in said head assembly for receiving and transfering wash fluid to said wash fluid discharge head, wash fluid actuated rotary drive meAns mounted on said head assembly externally of said passage, a fluid feed passage extending from said first passage to said drive means, and transmission means connected to said drive means to effect simultaneous rotational movement of said head assembly about said first axis, and said wash fluid discharge head about said second axis, said transmission means including means for effecting intermittent accelerations or decelerations in the rotational speed of said wash fluid discharge head relative to the rotational speed of said head assembly.

2. A machine as claimed in claim 1, wherein said transmission means comprise a static shaft, a first gear mounted for rotation on said shaft, a second gear mounted for driving said wash fluid discharge head and meshing with said first gear, a third gear secured on said shaft, reduction gear means connecting said drive means to said third gear for causing rotation of said head assembly around said shaft, means resisting rotation of said first gear by said second gear so that said second gear is driven inconsequence of the rotation of said head assembly, a rotary lobed element connected for driving said first gear, and striker means mounted in said head assembly for repeated engagement with said lobed element during rotation of the assembly whereby intermittent accelerations or decelerations of said first and second gears are effected.

3. A machine as claimed in claim 2, wherein the means resisting the rotation of the first gear comprises a friction clutch.

4. A machine as claimed in claim 2, wherein the means resisting the rotation of the first gear comprises a worm meshed with a worm wheel mounted for rotation with the first gear.

5. A machine as claimed in claim 4, wherein the worm is mounted on a spindle connected through a gear train to a further spindle carrying said lobed element, said further spindle being disposed radially with respect to said static shaft.

6. A machine as claimed in claim 2 in which the means mounting the head assembly for rotation comprises a pipe having a flange at one end adapted to bolted to a flange of a wash fluid supply pipe, said pipe comprising at its other end an internal support member to which the upper end of said static shaft is coaxially secured, said other end being received within a tubular inlet portion of said head assembly.

7. A machine as claimed in claim 6, wherein said pipe is divided into two annular portions and wherein said annular portions are connected by a friction clutch.

8. A machine for washing the interior surface of a hollow structure, comprising, in combination, a head assembly having a body member having an inlet passage, an outlet passage defining a bore a passage interconnecting said inlet and outlet passages, a first inner wall dividing said passages from a gear chamber, a second inner wall dividing said gear chamber from a Pelton wheel compartment having an exhaust part therein, an inlet pipe received at one end in said inlet chamber for rotation of said body with respect thereto, a flange on the other end of said inlet pipe for secural to a flange of a wash fluid supply pipe, a thrust bearing located at a transverse wall of said body member beneath said first inner wall, a sealing gland mounted in said first inner wall in axial alignment with said, thrust bearing, a static shaft carrying at its lower end the weight of said body through said thrust bearing and extending upwardly through said sealing gland, means supporting the upper end of said shaft coaxially in said inlet pipe, a first gear mounted for rotation on said static shaft a second gear meshing with said first gear and operatively connected through sealing means in said first inner wall with a wash fluid discharge head mounted for rotation in said outlet bore, a third gear secured on said static shaft, a Pelton wheel mounted for rotation in said Pelton Wheel compartment, reduction gear means connecting said Pelton wheel to said third gear for causing rotation of said head assembly around said shaft means resisting rotation of the first gear by said second gear, so that said second gear is driven in consequence of the rotation of said head assembly, a rotary lobed element connected for driving said first gear, striker means mounted in said head assembly for repeated engagement with said lobed element whereby intermittent accelerations or decelerations of said first and second gears are effected, and means defining a fluid feed passage extending between one of said first mentioned passages and said Pelton Wheel compartment and terminating in a nozzle or nozzles disposed for directing impulse jets at the buckets of the wheel.

9. A machine as claimed in claim 8, wherein the means resisting the rotation of the first gear comprises a friction clutch.

10. A machine as claimed in claim 8, wherein the means for resisting the rotation of the first gear comprises a worm meshed with a worm wheel mounted for rotation with the first gear.

11. A machine as claimed in claim 8, wherein said Pelton wheel compartment is mounted at the lower end of the head assembly and wherein the third gear is driven by a pinion connected to said Pelton wheel through a two stage worm and wheel reduction gear train located in a compartment intermediate said transverse wall and second inner wall.

12. A machine as claimed in claim 8, wherein said wash fluid discharge head is connected to said second gear through means comprising a friction clutch.

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