EP2556896A2 - Buse de nettoyage de réservoir - Google Patents

Buse de nettoyage de réservoir Download PDF

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Publication number
EP2556896A2
EP2556896A2 EP12179350A EP12179350A EP2556896A2 EP 2556896 A2 EP2556896 A2 EP 2556896A2 EP 12179350 A EP12179350 A EP 12179350A EP 12179350 A EP12179350 A EP 12179350A EP 2556896 A2 EP2556896 A2 EP 2556896A2
Authority
EP
European Patent Office
Prior art keywords
bearing
rotation
shaft
axis
nozzle head
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP12179350A
Other languages
German (de)
English (en)
Inventor
Christian Heid
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Lechler GmbH
Original Assignee
Lechler GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Lechler GmbH filed Critical Lechler GmbH
Publication of EP2556896A2 publication Critical patent/EP2556896A2/fr
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B3/00—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements
    • B05B3/02—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements
    • B05B3/04—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements driven by the liquid or other fluent material discharged, e.g. the liquid actuating a motor before passing to the outlet
    • B05B3/0417—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements driven by the liquid or other fluent material discharged, e.g. the liquid actuating a motor before passing to the outlet comprising a liquid driven rotor, e.g. a turbine
    • B05B3/0429—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements with rotating elements driven by the liquid or other fluent material discharged, e.g. the liquid actuating a motor before passing to the outlet comprising a liquid driven rotor, e.g. a turbine the rotating outlet elements being directly attached to the rotor or being an integral part thereof
    • B05B3/043—Rotor nozzles

Definitions

  • the invention relates to a tank cleaning nozzle having a housing, a shaft rotatably mounted about a first axis of rotation in the housing and at least one nozzle head rotatably mounted about a second axis of rotation with at least one outlet opening for fluid to be sprayed, wherein the second axis of rotation arranged substantially perpendicular to the first axis of rotation is and a drive unit in the housing for driving the shaft about the first axis of rotation and for driving the nozzle head about the second axis of rotation.
  • Known tank cleaning nozzles generally have a turbine wheel which can be rotated about a first axis of rotation and which then rotates a nozzle head about a second axis of rotation via a speed-reducing transmission.
  • the nozzle head may for example be provided with full jet nozzles, in order to achieve a satisfactory cleaning of the then far away from the nozzle head inner surfaces of the tank even with large tanks.
  • Such tank cleaning nozzles are also referred to as jet cleaner.
  • the required due to the high speed of the turbine wheel Intermediate gearbox makes the known tank cleaning nozzles complicated in construction and also relatively heavy and large.
  • a tank cleaning nozzle to be provided with a simple structure.
  • a tank cleaning nozzle with a housing, a shaft mounted about a first axis of rotation and at least one rotatably mounted about a second axis of rotation nozzle head with at least one outlet for fluid to be sprayed, wherein the second axis of rotation is arranged substantially perpendicular to the axis of rotation, and with a drive unit in the housing for driving the shaft about the first axis of rotation and for driving the nozzle head about the second axis of rotation, wherein the drive unit comprises a turbine wheel non-rotatably connected to the shaft and wherein the turbine wheel and the shaft each have a continuous one Have central bore to provide in the housing a first, via the turbine wheel leading flow path and a second, via the respective center bores leading flow path.
  • the speed of the turbine wheel can be kept low and, surprisingly, the turbine wheel can still apply such large torque to both the shaft connected to the turbine wheel and the first axis of rotation as well as to rotate the nozzle head about the second axis of rotation.
  • Tank cleaning nozzle is that due to the second, not on the turbine wheel leading flow path, a speed of the turbine wheel with increasing fluid pressure does not increase or insignificant. Therefore, no braking devices are required in order to keep the rotational speeds of the nozzle head in a range in which the so-called wiping effect, in which the generated cleaning jet passes too quickly over the surfaces to be cleaned, even under greatly varying fluid pressure. Due to the two flow paths in the housing, the speed of the turbine wheel can be kept so low that expensive reducers can be omitted.
  • the shaft is rotatably connected to a concentric with the second axis of rotation arranged bearing pin on which the nozzle head is rotatably mounted. In this way, can be completely dispensed with within the housing on a transmission, since the shaft is fixedly connected to the bearing pin arranged perpendicular to the shaft. In this way, a simple, less disturbance-sensitive arrangement can be achieved.
  • the nozzle head is annular and mounted rotatably on the bearing journal.
  • the bearing journal has a cavity, which is connected to the first flow path and the second flow path.
  • the housing is provided on its outside with a concentric with the first axis of rotation arranged first gear.
  • a rotation of the nozzle head about the second axis of rotation can be generated. Since the gear is arranged on the outside of the housing, its diameter can be made very large, so that also a low susceptibility to contamination is given. The arrangement on the outside of the housing prevents contamination also by the fact that the gear is not flowed around to be sprayed fluid.
  • the gear is designed as a crown wheel.
  • the nozzle head is provided on its outer side with a second gear disposed concentric with the second axis of rotation, which meshes with the first gear.
  • At least one sliding bearing is provided for supporting the shaft on the housing, the bearing gap is acted upon in spraying with the liquid to be sprayed.
  • the effect of a hydrostatic bearing is achieved without an external pump is required to supply the bearing gap with liquid to be sprayed.
  • the bearing gap is fluid lubricated immediately after pressurizing the housing with pressurized, liquid to be sprayed and as a result, immediately after applying the housing with liquid to be sprayed friction in the sliding bearing strong and wear substantially reduced to zero.
  • the plain bearing is advantageously designed as a thrust bearing, wherein such a thrust bearing is then acted upon by the liquid to be sprayed in order to reduce friction and wear substantially to zero.
  • At least one sliding bearing is provided for supporting the nozzle head on the bearing journal, the bearing gap is acted upon in spraying with the liquid to be sprayed.
  • the nozzle head is thus rotatably mounted by means of a sliding bearing, which has the effect of a hydrostatic bearing with extremely low friction after switching on the liquid supply.
  • the torque to be applied by the turbine wheel can thereby remain relatively low and as a result can be dispensed with a complex gear between the turbine wheel, shaft, journals and nozzle head. In particular, can be dispensed with a reducer.
  • each of the plain bearings both has a bearing surface lying concentrically to the second axis of rotation and a bearing surface lying perpendicular to the second axis of rotation and wherein the bearing gaps adjacent to the concentric and vertical bearing surfaces are acted upon in the spraying operation with the liquid to be sprayed.
  • the nozzle head is held on the bearing journal by means of two thrust bearings, but immediately after being exposed to liquid to be sprayed have the effect of a hydrostatic bearing and as a result are very low friction.
  • the nozzle head is thereby not only friction mounted rotatably mounted on the journal but at the same time fixed in the axial direction of the journal. Since also arranged perpendicular to the second axis of rotation bearing gaps are acted upon by the liquid to be sprayed, causes an axial positional deviation of the nozzle head on the journal no significant additional friction.
  • the nozzle head is thus stored extremely smooth.
  • the vertical bearing surfaces are arranged adjacent to the side surfaces of the annular nozzle head.
  • the nozzle head is annular and arranged on a rotatably connected to the shaft hollow bearing pin, wherein between the nozzle head and the bearing pin an annular space is defined, which is completed laterally by means of the bearing gaps of the plain bearing.
  • the nozzle head is provided with at least one full jet nozzle which is in flow communication with the annular space.
  • the bearing journal which is non-rotatably connected to the shaft is provided on its side opposite the nozzle head with respect to the shaft with a counterweight or a further nozzle head rotatable about the second rotational axis.
  • the shaft can be balanced with the bearing pin disposed about the first axis of rotation, so that the tank cleaning nozzle can be operated in any mounting position, since a generated by the weight of the nozzle head torque about the first axis of rotation by that of the weight of the counterweight generated torque is compensated.
  • FIG. 1 shows a partially sectioned view of a rotating nozzle assembly 10.
  • the nozzle assembly 10 has a relative to a merely schematically indicated connecting line 12 fixed housing 14, which consists of an upper half 16 and a lower half 18.
  • Der Gescousedeckel 12 ist in dem Genosuse 16 anorg.
  • the connection line 12 is screwed into the upper half 16 of the housing 14.
  • the lower half 18 is bolted to the upper half 16.
  • a shaft 20 is rotatably mounted and at one, the housing 14 opposite free end of the shaft 20 is a nozzle head 22 with a total of three individual nozzles 24, 26 and 28 is provided.
  • Each of the nozzles 24, 26, 28 defines an exit opening through which fluid to be sprayed is discharged.
  • the nozzles 24, 26, 28 are each, see also Fig. 2 , formed as a flat jet nozzles and thereby generate a Sprühf kauer, which extends substantially over 360 ° in the plane of the Fig. 1 extends.
  • the nozzle assembly 10 can thereby be used for example as a tank cleaning nozzle.
  • the nozzle head 22 is screwed onto the free end of the shaft 20 and secured in position on the shaft 20 by means of a locking pin 30.
  • the shaft 20 extends into the housing 14 and is rotatably mounted in the housing 14 by means of a bearing bush 32, which consists for example of Teflon.
  • the bushing 32 is provided on its, the shaft 20 facing the inside with a circumferential lubricating pocket 34 which communicates with a radially extending bore 36 in the shaft 20 in fluid communication. As soon as liquid is present in the connecting line 12, this fluid is also forced in through the radial bore 36 in the shaft 20 and into the lubricating pocket 34.
  • the radial bearing gap 38 is formed between an inner radial bearing surface of the bearing bush 32 and an outer periphery of the shaft 20.
  • the thrust bearing 40 is between an in Fig. 1 overhead thrust bearing surface of the bearing bush 32 and a in Fig. 1 below lying thrust bearing surface of a lying within the housing 14, extending in the radial direction shoulder 42 of the shaft 20 is formed.
  • Both the radial bearing gap 38 and the axial bearing gap 40 are supplied with liquid immediately after liquid has passed from the connecting line 12 into the interior of the shaft 20. Both the thrust bearing surface and the radial bearing surface are thus fluid-lubricated, and the shaft 20 is thereby mounted in the bearing bush 32 in a low-friction and essentially wear-free manner.
  • the shaft 20 is also mounted in the housing 14 by means of a further bearing bush 44, which is provided in an integrally connected to the shaft 20 turbine wheel 46.
  • the bushing 44 receives a journal 48 of a swirl insert 50 which is fixedly secured to the housing 14.
  • a radial bearing for the shaft 20 and the turbine 46 is formed.
  • the swirl insert 50 is clamped between the upper half 16 and the lower half 18 of the housing 14 and thereby secured to the housing 14.
  • the fan nozzles 24, 26, 28 in the nozzle head 22 are aligned neutrally and thus contribute by the dispensed spray neither to an increase nor to a reduction of the rotation generated by the turbine 46.
  • the Sprühfambaer, which are output from the fan nozzles 24, 26, 28, thus lie in or symmetrical to a plane, which includes the central longitudinal axis 52 of the nozzle assembly 10.
  • the dispensing of a spray fan through the fan nozzles 24, 26, 28 does not thereby result in a torque about the central longitudinal axis 52.
  • any nozzles can be used in the invention.
  • a second flow path provided, starting from the connecting line 12 leads through a central bore 54 in the swirl insert directly into the interior of the shaft 20 and then to the nozzle head 22. Liquid, which is passed through this second flow path, does not pass through the turbine wheel 46 and thus does not contribute to a rotational movement of the nozzle head 22.
  • Fig. 2 shows a view of the nozzle assembly 10 of Fig. 1 in an exploded view.
  • the upper housing half 16 is provided with an internal thread 56 into which an external thread 58 can be screwed to the lower housing half 18.
  • the swirl insert 50 is firmly clamped between the housing halves 16, 18.
  • the swirl insert 50 has a total of six swirl holes 60, which are inclined in the same direction in the circumferential direction. Above the swirl insert 50 pending liquid is thereby obliquely deflected by the swirl holes 60, strikes the turbine wheel 46 and thereby causes a rotational movement of the turbine wheel 46 about the central longitudinal axis 52nd
  • the swirl insert 50 is provided with the bearing pin 48 which is pierced concentrically to the central longitudinal axis 52 by means of the through hole 54.
  • the bearing pin 48 extends into the bearing bush 44.
  • the bushing 44 has a cylindrical portion and a circumferential projection which is received in a mating recess in the top of the turbine wheel 46.
  • the turbine wheel 46 is provided with a total of ten drive holes 62, which are arranged inclined to the central longitudinal axis 52. In this case, the angle of inclination of the drive bores 62 is directed opposite to the angle of inclination of the swirl bores 60, as for example in FIG Fig. 8 can be seen.
  • the turbine wheel 46 is formed integrally with the hollow-bored shaft 20 and also has a central bore into which the bearing bush 44 is inserted.
  • the shaft 20 is provided in its, adjoining the turbine wheel 46 area with a total of six radially arranged slots 64.
  • An extension direction of the elongated holes is parallel to the central longitudinal axis 52.
  • liquid which has passed the drive bores 62 in the turbine wheel 46 can reach the interior of the hollow-bored shaft 20 and from there to the nozzle head 22.
  • a first flow path for liquid from the connecting line 12 thus leads via the swirl bores 60 in the swirl disk 50, through the drive bores 62 in the turbine wheel 46 and then through the elongated holes 64 into the interior of the hollow-bored shaft 20 and from there into the nozzle head 22 and the flat jet nozzles 24, 26, 28.
  • the shaft 20 is provided with the extending in the radial direction, circumferential shoulder 42, the turbine facing away from the bottom forms a thrust bearing surface 66 of a thrust bearing.
  • the shaft 20 is inserted into the bearing bush 32, which also has a projecting in the radial direction, circumferential projection whose top forms a thrust bearing surface.
  • a cylindrical portion of the bushing 32 is inserted into a bearing bore 68 in the lower half 18 of the housing.
  • the circumferential projection 42 with its bearing surface 66 and the top of the bearing bush 32 form a thrust bearing for the shaft 20, which is parallel to the central longitudinal axis 52 and in the representation of Fig. 1 picks up downward forces.
  • FIG. 3 shows the shaft 20 with the turbine 46 in a view obliquely from above. It can be seen that the drive bores 62 are inclined in the circumferential direction in the disk-shaped turbine wheel 46 are introduced to a central longitudinal axis. In addition, all drive bores 62 have a circumferentially extending extension 70.
  • the extension 70 is formed in that an end mill, which is dipped obliquely into the disk-shaped turbine wheel 46 for forming the drive bores 62, is immersed once again at different angles or, for example, parallel to the central longitudinal axis in the upper region of the drive bores 62.
  • Fig. 4 shows a view of the shaft 20 and the turbine wheel 46 obliquely from the side.
  • a total of four radial bores 36 are provided in the shaft 20, of which in the illustration of Fig. 2 only two are visible.
  • these radial bores 36 provide fluid lubrication of the thrust bearing and the radial bearing between the shaft 20 and the bearing bush 32, see Fig. 1 ,
  • FIG. 5 shows a view of the turbine wheel 46 with the hollow-bored shaft 20 from above. Good to see is the continuous interior 72 of the hollow-drilled shaft 20, can pass through the liquid directly from the connecting line through the central bore 54 of the swirl insert 50 and also through the drive holes 62 of the turbine wheel 46 and the slots 64 to the nozzle head 22, see Fig. 1 ,
  • the presentation of the Fig. 6 shows a view on the cutting plane A - A in Fig. 5 , In Fig. 6 Good to see the oblique to the central longitudinal axis 52 extending drive holes 62 and the extensions 70 at the upstream end of the drive holes 62nd
  • the presentation of the Fig. 7 shows the swirl insert 50 in a view obliquely from above.
  • the central bore 54 is disposed concentric with the generally disc-shaped swirl insert 50 and is located at the bottom of a depression 74 which is also concentric with the swirl insert 50.
  • the top of the swirl insert 50 is, see Fig. 1 , slightly convex.
  • the swirl bores 60 are arranged in the region of the transition between the convex-shaped section 76 and an outer, disk-shaped section 78 of the swirl insert 50.
  • FIG. 8 shows an enlarged, sectional representation of the swirl insert 50 and the turbine wheel 46 with a portion of the shaft 20 in a partially sectioned view.
  • the swirl bores 60 in the swirl insert 50 are inclined in opposite directions to the drive bores 62 in the turbine wheel 46. Seen in the circumferential direction, the extensions 70 of the drive bores 62 in the turbine wheel 46 are arranged only on one side on the drive bores 62. Extensions 70 at the upstream end of drive bores 62 facilitate startup of turbine wheel 46 because the full cross-section of a liquid jet exiting from swirl bore 60 may penetrate into drive bores 62 when drive bore 62 is approximately in the in-hole Fig. 8 shown position is arranged relative to the swirl hole 60.
  • the center bore 54 has the positive effect that a flow within the cavity of the shaft 20 is only slightly turbulent and thus the jet pattern of the fan nozzles 24, 26, 28 is sharply defined. As a result, the cleaning effect of the spray fan output by the fan nozzles 24, 26, 28 as well as their throw is significantly improved. As already stated, the center bore 54 also ensures an equalization of the rotation of the hollow shaft 20, even with increasing fluid pressure.
  • center bore 54 in the swirl insert 50 also ensures that any particles present in the liquid supplied are passed directly into the cavity of the shaft 20 and thus to the fan nozzles 24, 26, 28 and thereby not in the bearing gap between the bearing pin 48 of the Swirl insert 50 and the bearing bush 44 in the turbine wheel 46 or in the radial bearing gap 38 or the thrust bearing 40 can pass between the bearing bush 32 and the shaft 20, see Fig. 1 ,
  • the presentation of the Fig. 9 shows a tank cleaning nozzle 100 in exploded view.
  • the tank cleaning nozzle 100 has a two-part housing with an upper housing part 102 and a lower housing part 104.
  • the lower housing part 104 is provided with a threaded flange 106, which can be screwed into a matching thread in the upper housing part 102.
  • the upper housing part 102 is provided with an internal thread 108 for connecting a supply line for fluid to be sprayed.
  • the Upper housing part 102 and the lower housing part 104 are each provided laterally with flats to attach a fork wrench to the housing can.
  • the lower housing part is provided on its underside with a gear formed as a crown gear 110, the function of which will be explained below.
  • a drive unit 112 is arranged, which has a swirl insert 114, a first bearing bush 116, a turbine wheel 118 which is integrally connected to a shaft 120 and a second bearing bush 122.
  • the drive unit 112 is like that of the Fig. 1 to 8 described drive unit of the rotating nozzle assembly 10 is formed, so that a further explanation is omitted.
  • the shaft 120 is at its in Fig. 9 lower end provided with an external thread 124 which can be screwed into a matching internal thread 126 on a journal 128. In this way, the shaft 120 and the bearing pin 128 can be rotatably connected to each other.
  • the shaft 120 is rotatably mounted in the housing 102, 104 together with the turbine wheel about a first axis of rotation 130.
  • the journal 128 is rotatable together with the shaft 120 about this first axis of rotation 130 and defines itself a second axis of rotation 132 around which then a nozzle head 134 is rotatably mounted on the bearing journal 128.
  • the first axis of rotation 130 and the second axis of rotation 132 are perpendicular to each other and intersect.
  • the journal 126 is provided with a blind hole, see also Fig. 11 that differ from one in Fig. 11 left front lying concentric concentric with the second axis of rotation 132 in the bearing pin 128 hineinerstreckt.
  • the blind hole ends behind the area of the internal thread 126.
  • the shaft 120 is also hollow, so that liquid to be sprayed on the cavity of the shaft 120 in the blind hole of the journal 128 and then ultimately reach the nozzle head 134.
  • the journal 128 is provided with a bearing portion 136 which is provided with a plurality of radially extending through holes 138 which connect the blind hole in the bearing journal 128 with an area surrounding the bearing portion 136.
  • an annular space 140 is arranged, which is formed on the one hand by the bearing portion 136 and on the other hand by the inside of an annular portion 142 of the nozzle head 134.
  • the liquid to be sprayed passes and from there via through openings in the wall of the annular member 142 in two full-jet nozzles 144, 146 which are mounted on the outer periphery of the annular member 142 of the nozzle head 134.
  • the full jet nozzles 144, 146 may be welded or bolted to the annular member 142, for example.
  • the nozzle head 134 is rotatably mounted about the second axis of rotation 132 on the bearing pin 128, wherein the bearing pin 128 in turn rotates together with the shaft 120 and the turbine wheel 118 about the first axis of rotation 130.
  • the nozzle head is provided at its radially inner end with respect to the first axis of rotation 130 with a gear 148, which in the assembled state of the tank cleaning nozzle 100, see Fig. 11 , with the crown gear 110 meshes with the housing lower part 104.
  • the gear 148 thereby rolls during rotation of the journal 128 about the first axis of rotation 130 on the crown gear 110 and thereby causes a Turning the nozzle head 134 on the journal 128 about the second axis of rotation 132.
  • the crown gear 110 and the gear 148 on the nozzle head 134 are substantially the same size, for example, but the number of teeth is different by one tooth or a few teeth to achieve that the full-jet nozzles 144, 146 after a full rotation of the journal 128 about the first axis of rotation 130 in a different position than at the beginning of the revolution. This ensures that a tank to be cleaned with the tank cleaning nozzle 100 is completely and thoroughly cleaned when a certain number of revolutions of the journal 128 and thus of the nozzle head 134 has taken place.
  • the annular component 142 of the nozzle head 134 is mounted on the bearing section 136 of the bearing journal 128 by means of two bearing bushes 150, 152.
  • the bushings 150, 152 form together with the side surfaces of the annular member 142 each have a thrust bearing, see also Fig. 11 ,
  • the nozzle head 134 is thereby fixed in the axial direction to the second axis of rotation 132 on the bearing journal 128.
  • the blind hole 154 in the journal 128 is at its front side, in Fig. 11 lying left, closed with a screw plug 156.
  • the closure screw 156 seals on the one hand, the blind hole 154 and on the other ensures that the bearing bushes 150, 152 and thus also the annular member 142 remain in their predetermined axial position on the journal 128. This ensures at the same time that the crown gear 110 and the gear 148 on the annular member 142 remain in engagement with each other.
  • the thrust bearings formed between the bushings 150, 152 and the annular member 142 are formed as a fluid-lubricated sliding bearing and, as soon as the tank cleaning nozzle 100th is acted upon with liquid to be sprayed, subjected to pressurized liquid.
  • the liquid to be sprayed penetrates into the bearing gap between the bearing bushes 150, 152 and the annular member 142 and thus ensures immediately after being applied with liquid to be sprayed for the effect of a hydrostatic slide bearing.
  • both the concentric to the second axis of rotation bearing gaps and the respective perpendicular to the second axis of rotation 132 bearing gaps are acted upon with liquid to be sprayed so that the nozzle head 134 very friction and substantially wear-free on the bearing portion 136 and the bearing bushes 150, 152 stored is.
  • the torque applied by the turbine wheel 118 is thereby sufficient to rotate the journal 128 about the first axis of rotation 130 and simultaneously to cause the rotation of the nozzle head 134 with the full jet nozzles 144, 146 about the second axis of rotation 132.
  • a sliding bearing between the shaft 120 and the bearing bush 122 is fluid lubricated and immediately after switching on the supply of liquid to be sprayed the effect of a hydrostatic sliding bearing, which is substantially free of friction.
  • the special design of the drive unit 112, based on the Fig. 1 to 8 has been explained, ensures that even with increasing pressure of the liquid to be sprayed, a speed of the turbine wheel 118 does not rise or only slightly.
  • the shaft 120 is additionally secured by screwing its thread 124 into the internal thread 126 on the bearing pin 128 by a stud 158 to ensure the rotationally fixed connection between the shaft 120 and journal 128.
  • the tank cleaning nozzle 100 only one nozzle head 134 with two full-jet nozzles 144, 146.
  • a further, similarly constructed nozzle head 134 can readily be arranged. This further nozzle head 134 would then also be rotated about the second axis of rotation 132 via an engagement in the crown gear 110.
  • the in Fig. 11 right end of the journal 128 solid and designed as a counterweight 160.
  • the counterweight 160 ensures that the tank cleaning nozzle 100 can be operated in any mounting position, since the torque generated by the weight of the nozzle head 134 about the first axis of rotation 130 is always compensated by the counterweight 160.
  • Liquid to be sprayed enters the upper housing part 102 via a fluid supply line, not shown, and flows through obliquely arranged bores in the swirl insert 114.
  • the quantities of liquid emerging from the obliquely arranged bores of the swirl insert 114 strike the turbine wheel 118 arranged in the opposite direction to the bores in the swirl insert 114 Has through holes.
  • the turbine wheel 118 is thereby rotated and takes the shaft 120 with.
  • the swirl insert 114 is provided with a central bore 162, can pass over the liquid to be sprayed past the turbine wheel directly into the hollow shaft 120.
  • the liquid Downstream of the turbine wheel 118, the liquid passes through radial bores in the hollow shaft 120 in the interior of the hollow shaft 120.
  • the liquid to be sprayed then flows through the hollow shaft 120 and into the blind hole 154 in the journal 128. As has been stated, is to be sprayed with the Fluid in the shaft 120 and their sliding bearing on the housing base 104 is acted upon.
  • the liquid to be sprayed then passes through the through-openings 138 into the annular space 140 and from there into the nozzle channels of the full-jet nozzles 144, 146. From the full jet nozzles 144, 146, a concentrated full jet emerges, which has a high range and thus even far away inner walls of tanks or containers can still clean.
  • a jet director 145 can be provided in the full-jet nozzles 144, 146, in order to improve the quality of the full jet and in particular its range, wherein the jet judge in Fig. 11 is shown only schematically.

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EP12179350A 2011-08-12 2012-08-06 Buse de nettoyage de réservoir Withdrawn EP2556896A2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011080879A DE102011080879A1 (de) 2011-08-12 2011-08-12 Tankreinigungsdüse

Publications (1)

Publication Number Publication Date
EP2556896A2 true EP2556896A2 (fr) 2013-02-13

Family

ID=46603785

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12179350A Withdrawn EP2556896A2 (fr) 2011-08-12 2012-08-06 Buse de nettoyage de réservoir

Country Status (2)

Country Link
EP (1) EP2556896A2 (fr)
DE (1) DE102011080879A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016102727A1 (de) 2015-08-17 2017-02-23 Netzsch-Feinmahltechnik Gmbh Reinigungsvorrichtung und produktverarbeitende Anlage

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3416732A (en) * 1967-06-05 1968-12-17 Purex Corp Ltd Washing apparatus for enclosed spaces
AU581645B2 (en) * 1984-03-09 1989-03-02 Yoram Shevach Water sprinkler
DE29705016U1 (de) * 1997-03-19 1997-05-15 Uelzena Milchwerke eG, 29525 Uelzen Anordnung einer Reinigungsdüse und einer Blindvorrichtung für die Reinigungsdüse
DE10006864B4 (de) * 2000-02-16 2006-02-09 Spraying Systems Deutschland Gmbh Reinigungsdüse

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016102727A1 (de) 2015-08-17 2017-02-23 Netzsch-Feinmahltechnik Gmbh Reinigungsvorrichtung und produktverarbeitende Anlage
WO2017028831A1 (fr) 2015-08-17 2017-02-23 Netzsch-Feinmahltechnik Gmbh Dispositif de lavage et installation de traitement de produit
US11141745B2 (en) 2015-08-17 2021-10-12 Netzsch-Feinmahltechnik Gmbh Cleaning device and product processing system

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