EP0247532A2 - Dispositif de nettoyage pour réservoirs et similaires - Google Patents

Dispositif de nettoyage pour réservoirs et similaires Download PDF

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Publication number
EP0247532A2
EP0247532A2 EP87107444A EP87107444A EP0247532A2 EP 0247532 A2 EP0247532 A2 EP 0247532A2 EP 87107444 A EP87107444 A EP 87107444A EP 87107444 A EP87107444 A EP 87107444A EP 0247532 A2 EP0247532 A2 EP 0247532A2
Authority
EP
European Patent Office
Prior art keywords
bearing
spray head
cleaning device
bearing housing
spray
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Withdrawn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
EP87107444A
Other languages
German (de)
English (en)
Other versions
EP0247532A3 (fr
Inventor
Helmut Becker
Desider Boda
Alois Feiner
Roland Ponterlitschek
Erich Appt
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APPT E
Original Assignee
APPT E
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 APPT E filed Critical APPT E
Publication of EP0247532A2 publication Critical patent/EP0247532A2/fr
Publication of EP0247532A3 publication Critical patent/EP0247532A3/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Withdrawn legal-status Critical Current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
    • B05B3/008—Spraying or sprinkling apparatus with moving outlet elements or moving deflecting elements comprising a wobbling or nutating element, i.e. rotating about an axis describing a cone during spraying
    • 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
    • B05B3/0409—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 with moving, e.g. rotating, outlet elements
    • B05B3/0418—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 with moving, e.g. rotating, outlet elements comprising a liquid driven rotor, e.g. a turbine
    • B05B3/0422—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 with moving, e.g. rotating, outlet elements comprising a liquid driven rotor, e.g. a turbine with rotating outlet elements
    • B05B3/0445—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 with moving, e.g. rotating, outlet elements comprising a liquid driven rotor, e.g. a turbine with rotating outlet elements the movement of the outlet elements being a combination of two movements, one being rotational
    • 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
    • B05B3/0495—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 the liquid or other fluent material discharged powering several motors, e.g. several turbines
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B08—CLEANING
    • B08B—CLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
    • B08B9/00—Cleaning hollow articles by methods or apparatus specially adapted thereto 
    • B08B9/08—Cleaning containers, e.g. tanks
    • B08B9/093—Cleaning containers, e.g. tanks by the force of jets or sprays
    • B08B9/0936—Cleaning containers, e.g. tanks by the force of jets or sprays using rotating jets

Definitions

  • the topping can consist of residues of the liquid or its ingredients that have adhered to it due to adhesion or due to its own stickiness or that have deposited there as a result of a drying process.
  • substances from the liquid that either float to the surface of the liquid or sink in the liquid and then settle on the container walls. Even if the type of liquid is not changed, it is often necessary or desirable for the container to be cleaned of the remains of the last filling before refilling.
  • cleaning devices are used with which a working medium, which usually consists of water with or without cleaning additives, is sprayed under high pressure from spray nozzles onto the container walls, where the spray jets usually blow off the coating from the container walls due to their kinetic energy and / or rinse off.
  • a working medium which usually consists of water with or without cleaning additives
  • a known cleaning device for containers and the like has a sleeve which serves as a holder.
  • a shaft is supported in the sleeve and protrudes from the sleeve at the lower end.
  • a bearing journal oriented transversely to the shaft axis, on which a spray head is rotatably mounted.
  • This has a spray nozzle at each of two diametrically located circumferential points, the outlet direction of which is aligned radially with respect to the bearing journal.
  • a bevel gear is arranged at the lower end of the sleeve.
  • the spray head faces the shaft facing side also on a bevel gear that comes with the bevel gear on the sleeve.
  • the two bevel gears have different numbers of teeth.
  • the shaft of the spray head At the upper end of the sleeve there is an electric motor, the shaft of which is coupled to the shaft of the cleaning device. If this shaft is driven by the electric motor and the pivot pin is thereby pivoted around the shaft axis, the bevel gear of the spray head rolls on the bevel gear teeth of the sleeve. As a result, the spray head is rotated on the bearing journal when it is pivoted around the shaft axis.
  • This cleaning device requires a separate drive at the upper end of the sleeve.
  • the sleeve must therefore be made slightly longer than the desired immersion depth of the cleaning device.
  • the entire device is therefore at least by the height of the drive motor and a holding device higher than the minimum immersion depth of the cleaning device. If the room height is limited at the place of use, ie above the cleaning opening of the container, such a cleaning device cannot be used. Conversely, in the case of very flat containers, the cleaning device protrudes very far beyond the top of the container, where it must be held free-standing by the operator.
  • the drive mode for the shaft is generally designed as an electric motor. This must then be splash-proof to reduce the risk of accidents. This increases the price of the cleaning device considerably.
  • This cleaning device has a rigid transmission ratio between the rotational movement of the spray head and the pivoting movement of its bearing journal.
  • the alignment lines of the spray jets of the spray head therefore describe the cleaning device on the inner surface of an imaginary hollow sphere, in the center of which is arranged, a very specific spatial line pattern, the lines of which are evenly adjacent to each other at a certain distance.
  • this theoretical spray pattern which is based on a hollow sphere with a certain clear width, deviates even more from the requirements that are imposed on both the individual containers due to their geometric internal or hollow shape and their dimensions, and the covering due to their nature and adhesive properties to the cleaning device. In individual cases, this results in a disproportionately long period of use of the cleaning device with a correspondingly large consumption of work equipment and energy until the container walls are completely cleaned. If the working fluid is to be reused in order to reduce at least this proportion of consumption, this generally requires a not inconsiderable amount of cleaning work for the working fluid, because it must be prevented that residues of the detached coating get into the cleaning device and clog it, especially its spray nozzles.
  • the spray head is designed in the manner of a Seger wheel, in which the exit direction of the spray jets is oriented tangentially to the axis of rotation of the spray head, so that the spray jets exert a torque on the spray head.
  • the bearing pin for the spray head is arranged on a bearing housing, which in turn is rotatably mounted on a holder.
  • the bearing journal is aligned on the bearing housing radially to its axis of rotation, which thus simultaneously forms a pivot axis for the pivoting movement of the bearing journal and the spray head mounted thereon.
  • an angular drive one gear of which is coupled to the spray head and the other gear of which is coupled to the holder, so that when the spray head rotates as a result of a rolling movement of its toothing on the toothing of the holder, a torque is exerted on the bearing housing, that swings the bearing journal around with the spray head.
  • the flywheel serving as the drive would run at very high speeds when running freely, the spray jets resulting in the very high angular velocity then resulting in only a slight cleaning effect. For this reason, a brake device is installed in this cleaning device, through which the speed of the spray head and thus also the speed of the bearing housing is reduced. This inevitably destroys part of the flow energy of the working fluid.
  • the invention specified in claim 1 has for its object to provide a cleaning device for containers and the like, which enables a thorough cleaning of the container in an economical manner and which can also be easily adjusted to the requirements of different containers.
  • the spray nozzles lead to a certain extent wobble whose orientation in space is constantly changing. Because the drive of the spray head and the drive of the bearing housing are not mechanically coupled to one another, they can easily be adjusted separately to the requirements of different containers, for example by a lower pivoting speed of the bearing housing in relation to the speed of the spray head for containers with a larger clear width is set and this speed ratio is selected differently with a smaller clear width.
  • all spatial coordinates can be achieved by the spray jets without additional adjustment movements on the holder of the cleaning device being required.
  • An embodiment of the cleaning device according to claim 3 results in a bearing housing in which the connecting surfaces appear at both ends as flat circular surfaces or straight circular cylindrical surfaces, which is very favorable both for mechanical processing and for assembly.
  • a bearing housing that can be produced from a single cylindrical body, in which at least at one end flat circular surfaces or straight circular cylindrical surfaces appear, although flat surfaces are also possible at the other end, the outline of which, however, does Is ellipse. Since the mechanical processing and the assembly of the parts to be attached to them mostly anyway, if not exclusively, on the end face, the ellipse shape does not interfere.
  • An embodiment of the cleaning device according to claim 5 results in a drive with a very good hydraulic efficiency, so that especially when using the working medium as a driving means, the pressure loss in the working medium is very low and the greater part of the energy of the working medium for the cleaning effect of the Spray blasting is available. This increases the overall efficiency both with regard to the operating time of the cleaning device and with regard to the consumption of energy and work equipment.
  • the torque of the turbine is increased, so that a lower pressure drop in the working medium is required to overcome the resistances, in particular due to the friction on the bearing surfaces and the sealing surfaces.
  • the risk of pressure surges and vibrations in the working fluid is reduced.
  • the turbine is not equipped with a streamlined turbine blading in the narrower sense of the word, but rather is designed in the manner of a free-jet turbine, the blades of which do not reach the ideal shape.
  • the two turbines are hydraulically connected in series. This achieves a certain, if not rigid, coupling of the speeds, which, however, can still be changed by different design of the two turbines and the speed behavior caused thereby.
  • the two turbines are hydraulically connected in parallel. As a result, they can be operated largely independently of one another depending on the type of division of the working medium into the two partial streams and depending on the operating behavior of the division point and accordingly can also be set individually.
  • the additional spray nozzle can be used as a control nozzle. It can either be set in the same direction as the turbine, increasing the driving effect of the turbine, or it can be set in the opposite direction to the turbine can be set, whereby it reduces the drive effect of the turbine. In the latter case, the angular velocity of the pivoting movement of the bearing housing can be reduced to very low values, in extreme cases even to zero. In the former case, it is increased above the normal value. In addition, all intermediate values are of course possible.
  • At least one or more of the spray nozzles can be set so that these spray nozzles spray twice exactly axially parallel and perpendicularly to one revolution during one revolution and thus cover the entire inside of a hollow sphere in the center of which the cleaning device is thought to be arranged.
  • the spray nozzles can also be set so that the surface area of the cleaning opening of the container is not covered by the spray jets. Then there is no need for a separate cover for the cleaning opening, which noticeably facilitates the handling of the cleaning device when it is inserted into the container and when the cleaning device is in operation, without the working medium hitting the surroundings of the container.
  • a plurality of spray nozzles can be accommodated and adjusted to different desired or required directions.
  • the turbine of the spray head can be saved if, in individual cases, the good drive efficiency of the turbine compared to that of the spray nozzle drive is not important and the resulting reduction in the cost of the cleaning device is more important.
  • the turbine for the bearing housing is replaced by a spray nozzle drive, such as, for example, by the control nozzle according to claim 10 given is.
  • Such a mode of operation can also be considered as an alternative if one of the turbines fails and it cannot be replaced immediately, but the operation of the cleaning device cannot be interrupted until the replacement turbine has been procured.
  • the cleaning device 10 has a holder 11, a bearing housing 12 and a spray head 13.
  • the bearing housing 12 is pivotally mounted at one end by means of an axially and radially acting pivot bearing 14 on the holder 11.
  • the spray head 13 is rotatably supported by means of a pivot bearing 15 which also acts axially and radially.
  • the pivot axis 16 of the pivot bearing 14 and the axis of rotation 17 of the pivot bearing 15 intersect at an angle a of at least approximately 135 °.
  • the holder 11 has a short rod part 21 with a circular cross section.
  • the rod part 21 is offset at its free end and provided with an external thread 22.
  • a coupling sleeve 23 is screwed onto it. On its free end face, this has an internal thread as the receiving thread 24.
  • the cleaning device 10 can thus be screwed onto the end of an extension or holding rod 25, which is only indicated by dash-dotted lines in FIG. 1 and with which it can be securely held and guided even in deeper containers.
  • the coupling sleeve 23 with the receiving thread 24 offers the possibility of screwing the holding rod 25 only after the cleaning device 10 has been introduced into the cleaning opening of a container, so that the cleaning device 10 even in very confined spaces, in particular in a very small room height above the cleaning opening of the Container with which the support rod can be combined and, conversely, can also be separated from it again if the cleaning device 10 is to be removed from the container after the cleaning process has ended.
  • the rod part 21 has an inlet line 26 which starts as a centrally arranged blind hole from the free end of the rod part.
  • the coupling sleeve 23 has a through opening 27 aligned therewith.
  • the rod part 21 has two diametrically extending and perpendicular cross holes 28 which serve to pass on the working medium flowing through the inlet line 26.
  • the pivot bearing 14 is formed by a plurality of bearing parts which are partly connected to the holder 11 and partly to the bearing housing 12.
  • the end section of the rod part 21 facing away from the coupling sleeve serves as a bearing journal 31.
  • a circular cylindrical bearing disk 32 is fastened to the bearing journal 31, and preferably shrunk onto the bearing journal 31.
  • the peripheral surfaces 33 of the bearing journal 31 on both sides of the bearing disk 32 and its two flat end faces 34 form the radially or axially acting bearing surfaces of the pivot bearing 14 connected to the holder 11.
  • a spacer ring 37 is arranged between these two outer bearing washers 35 and 36.
  • the two bearing disks 35 and 36 and the spacer ring 37 are firmly screwed to one another and to the bearing housing 12 by means of a number of fastening screws 38, of which only four are shown in FIG. 2, with eight actually being present.
  • the inner circumferential surface 41 of the bearing disc 35 and the inner circumferential surface 42 of the bearing disc 36 form the radially acting bearing surfaces of the pivot bearing 14 which are connected to the bearing housing 12.
  • the end face 43 of the bearing disc 35 facing the inner bearing disc 32 and the corresponding end surface 44 of the bearing disc 36 form that axially acting bearing surfaces of the pivot bearing 14, which are connected to the bearing housing 12.
  • the inner circumferential surface 38 and 39 of the bearing washers 35 and 36 are matched to the circumferential surfaces 33 of the journal 31, while adhering to very tight tolerances that, in addition to their function as bearing surfaces, they can also perform the function of gap seals, which are achieved by the Prevent inlet line 26 and the transverse bores 28, which are passed through and are under high pressure, from escaping from the bearing points in large quantities along the journal 31 to the outside. This is supported by a correspondingly narrow tolerance of the Distance between the inner bearing plate 32 and the two outer bearing plates 35 and 36, which is done by coordinating the thickness of the spacer ring 37. It should be pointed out that, for the sake of clarity, these distances between the bearing surfaces have been shown larger in FIG. 1 than they actually are.
  • the leakage quantity emerging upwards in the direction of the rod part 21 mixes with the working fluid sprayed through the spray head 13.
  • the leakage quantity emerging downward first reaches a blind hole 45 in the bearing line 12 in the alignment of the bearing journal 31 and from there via a drain hole 46 to the outside. This prevents the build-up of excess pressure below the journal 1.
  • the interconnected outer bearing parts of the pivot bearing 14, namely the two bearing disks 35 and 36 and the spacer ring 37, are jointly surrounded on their outer circumferential surface by a cover sleeve 47 which seals these three bearing parts to the outside against the escape of the working medium.
  • the bearing plate 32 and the spacer ring 37 form not only parts of the pivot bearing 14, but also parts of the drive 18 for the bearing housing 12.
  • This drive 18 is designed as a turbine drive.
  • the bearing disk 32 is designed in its interior as a guide device or guide wheel 48 and the spacer ring 37 in its interior as an impeller 49 of the turbine 18 (FIG. 2).
  • the working fluid is supplied through the feed line 26 and exits through the transverse bores 28 into an annular space 51. From there, the working medium enters a number of guide channels 52 oriented tangentially to the annular space 51 and leaves them on the outside of the guide wheel 48 with a tangential component.
  • the impeller 49 there are an equal number of guide blades 52 to the number of guide channels 52, onto which the exiting from the guide channels 52 Work equipment strikes with a tangential component.
  • the working fluid flows out of the rotor blades 53 through guide channels 54 and then passes into axial drain channels 55, through which it is conducted to the bearing housing 12.
  • the guide channels 52 are formed by bores in the stator 48.
  • the guide channels 54 are formed by bores in the impeller 49, the outermost surface line of which is aligned at least approximately tangentially to the inner circumferential surface of the impeller 49.
  • the cylindrical bores running in a cross-sectional plane perpendicular to the swivel axis 16 are cut obliquely in an arc shape by the inner circumferential surface of the impeller 49 aligned coaxially to the swivel axis 16.
  • the remaining wall surface of the bores each forms a rotor blade 53 of the impeller 49.
  • the bearing housing 12 is formed by two at least approximately circular cylindrical bodies 56 and 57, which are called cylinder bodies 56 and 57 in the following for short. They adjoin one another in FIG. 1 for the sake of clarity, not shown, which is inclined relative to the cylinder axis of each of the two individual cylinder bodies 56 and 57 by half the angle by which the cylinder axes are inclined relative to one another, which is also the inclination angle or Intersection angle of the pivot axis 16 and the axis of rotation 17 corresponds.
  • the cylinder bodies 56 and 57 are either butt welded to one another or screwed to one another. In the latter case, the fastening screws 38, which connect the outer parts of the pivot bearing 14 to one another and to the bearing housing 12, can also be used for the connection of the two cylinder bodies 56 and 57.
  • the pivot bearing 14 is fastened to the free end face of the cylinder body 56.
  • the pivot bearing 13 is fastened to the free end face of the cylinder body 57.
  • connecting lines or connecting channels 58 and 59 are attached, which on the one hand connect to the drain channels 55 of the drive 18 and on the other hand to corresponding channels of the rotary bearing 15.
  • a spray nozzle 61 is arranged on the outside of the upper cylinder body 56, preferably in the plane in which the pivot axis 16 and the axis of rotation 17 lie. It has a muzzle tube 62, which is seated in a radially aligned through hole in the wall of a circular cylindrical support ring or adjusting ring 63.
  • the setting ring 63 can be removed from the cylinder body 58 by means of a hollow screw 64, but is connected in a liquid-tight manner.
  • the hollow screw 64 is screwed into a threaded hole 65 of the cylinder body 56, which is connected to one of the connecting channels 58.
  • the hollow screw 54 has at least one diametrically extending transverse bore for the outlet of the working medium in the cross-sectional plane of the orifice tube 62. In the same cross-sectional plane, there is a circumferential groove 67 on the inside of the adjusting ring 63, through which the working medium emerging from the mouths of the transverse bores 66 is guided to the mouth tube 62.
  • the axial through hole of the hollow screw 64 extends to the end of the screw head.
  • the hollow screw 64 is provided with an internal thread in which a threaded pin 68 is screwed. It is provided at its front end with a conical tip 69, by means of which the axial through hole of the hollow screw 64 can be closed or opened to a greater or lesser extent at the transition point to the transverse bores 66.
  • an eye 70 for this Cylinder body 56 protrudes outwards, as shown in FIGS. 1 and 2.
  • This eye 70 can either be integrally formed on the cylinder body 56 or welded to it.
  • the spray nozzle 61 can be set in any direction in a tangential plane to the pivot axis 16. Insofar as its spray direction has a peripheral component, the spray nozzle 61 acts as a control nozzle for the bearing housing 12. If this peripheral component of the spray nozzle or control nozzle 61 is oriented in the same direction as the direction of rotation of the drive turbine 18, it supports the pivoting movement of the bearing housing 12 generated by the drive turbine 18 Circumferential component of the control nozzle 61 is oriented in the opposite direction to the direction of rotation of the drive turbine 18, it counteracts this rotary movement.
  • control nozzle 61 Since the control nozzle 61 is at a certain distance from the pivot axis 16, which is greater than the center distance of the rotor blades 53, a counter torque can be generated with the control nozzle 61 depending on the strength of its spray jet, which reaches up to the torque of the drive turbine 18. As a result, the angular velocity of the bearing housing 12 can be set to a very low value down to zero if necessary.
  • the pivot bearing 15 is constructed similarly to the pivot bearing 14.
  • a bearing pin 71 which is connected to the spray head 13, has a circular cylindrical bearing disk 72.
  • the bearing disk 72 and the bearing pin 71 are made in one piece here.
  • the circumferential surfaces of the bearing pin 71 on both sides of the bearing disk 72 form the radially acting bearing surfaces and the two flat annular end faces of the bearing disk 72 form the axially acting bearing surfaces of the rotary bearing 15, which are connected to the spray head 13.
  • the two outer bearing disks 73 and 74 and the spacer ring 75 lying between them are connected to the bearing housing 12.
  • the inner ones Circumferential surfaces of the two bearing disks 73 and 74 represent the radially acting bearing surfaces and the end face of the two outer bearing disks 73 and 74 facing the inner bearing disk 72 respectively represent the axially acting bearing surfaces of the rotary bearing 15, which are connected to the bearing housing 12.
  • the rotary bearing 15 also serve here as parts of the drive 19 for the spray head 13.
  • This drive 19 is also designed as a turbine. Since here the working medium for driving the turbine 19 is fed through the external connecting channels 59 in the cylinder body 57 of the turbine 19, the spacer ring 75 form the stator and the bearing disk 72 form the impeller of the turbine 19. The impeller 77 is therefore acted upon on the outside.
  • connection channels 59 in the bearing housing 12 each connect an inflow channel 81, which extends in the axial direction, i.e. parallel to the axis of rotation 17 until it extends into the stator 78.
  • Another short inflow channel 81 which is located in the stator 78 in a cross-sectional plane, the surface normal of which is aligned parallel to the axis of rotation 17.
  • These inflow channels 82 are oriented at least approximately tangentially to the inner peripheral surface of the stator 78 (FIG. 3).
  • Each of the inlet channels 82 is followed by a guide channel 83 which is substantially narrower than the preceding inlet channel 82. As a result, this guide duct 83 acts like the nozzle of a free jet turbine.
  • the blades 85 are machined as recesses on the peripheral surface of the impeller 72.
  • a discharge channel 85 which is aligned radially to the axis of rotation 17.
  • the axial dimension is larger than the circumferential dimension by one to achieve the largest possible passage cross-section.
  • the drainage channels 85 open into a collecting channel 86 in the middle of the impeller 79. This collecting channel 86 continues in the axial direction in the journal 71 as a feed line 87 for the working fluid to the spray head 13.
  • the bearing pin 71 has at least one diametrically extending transverse bore 88 through which the working medium can pass from the feed line 87 into the spray head.
  • the feed line 87 in the bearing pin 71 is designed as a blind hole which ends beyond the transverse bore 88. At the opposite end of the journal 71, this blind hole on the other side of the collecting channel 86 is closed to the outside by means of a sealing plug 89. In the direction of escape of the journal 71, there is a blind hole 45 in the bearing housing 12 also on the end face facing the pivot bearing 15 with an outflow channel 46 through which the leakage quantity of the working fluid emerging from the pivot bearing 15 can flow away.
  • the number of guide channels 52 in the guide wheel 49 and the number of blades 53 in the impeller 49 are the same.
  • the number of rotor blades 84 is greater than the number of guide channels 83.
  • the impeller 79 has nine rotor blades 84 and the guide wheel 78 has eight guide channels 83.
  • this ratio can also be chosen differently.
  • the spray head 13 is roughly pot-shaped. It has a disk part 91 and an edge part or bead 92.
  • the disk part 91 is provided in the middle with a circular cylindrical through hole through which the end section 93 of the bearing pin 71 extends.
  • the end section 93 is opposite to that Bearing journal 71 set off so that the disk part 71 has a specific seat on the journal 71 in the axial direction.
  • the first part of the end section 93 is designed with a smooth peripheral surface.
  • the end section 93 is threaded toward the free end.
  • a washer 94 is slid onto it and a fastening nut 95 is firmly screwed on.
  • sealing means are used between the journal 71 and the disk part 91, which are not shown in detail in FIG. 1.
  • a circumferential groove 96 is present in the disk part 91, into which the working medium passes after exiting the transverse bore 88. From the circumferential groove 96, the working medium passes into a distributor line 97, which is formed in the spray head 13 shown in FIG. 1 as a diametrically continuous bore in the disk part 91, which is closed at both ends by a sealing plug 98.
  • a branch line 99 which leads to a spray nozzle 101 or 102, connects to the distributor line 97 in the bead 92.
  • the spray nozzle 101 is designed in the same way as the spray nozzle 61. Like this, it has a muzzle tube 62 on an adjusting ring 63, which is provided on the inside in the cross-sectional plane of the muzzle tube with a circumferential groove.
  • the spray nozzle 101 is fixed by means of a hollow screw 103 on a flat seat surface 104 on the edge bead 92 and, above all, liquid-tight.
  • the hollow screw 103 has an axial blind hole 105 which is connected to the stub 99. In the cross-sectional plane of the orifice tube 62, the hollow screw 103 in turn has a diametrically extending transverse bore 106.
  • the spray nozzle 102 is designed as a double nozzle. With it, two adjusting rings 63 sit axially one above the other, the mouth tubes 62 of which are set to different spray directions. The two adjusting rings 63 are clamped to the bead 92 by means of a hollow screw 107, which has a correspondingly greater length. Its blind hole 108 is connected to the stub 99. The hollow screw 108 has a diametrically extending transverse bore 109 in the cross-sectional plane of each of the two orifice tubes 62.
  • the longitudinal axis of the two spray nozzles 101 and 102 are both located in a common axial section plane. They are inclined by at least approximately 45 ° with respect to the axis of rotation 17. In the normal case, their spray tubes are also aligned in the common axial section plane, so that they are aligned twice perpendicular to the pivot axis 16 and in between twice parallel to the pivot axis 16 of the bearing housing 12 when the spray head 13 rotates. In between, they take appropriate intermediate positions. If necessary, the spray nozzles 101 and 102 can also be set to a different spraying direction, for example in order to avoid that the spray jets emerging from them can escape to the outside through a cleaning opening of the container to be cleaned which is around the axis of rotation 16.
  • the two drive turbines 18 and 19 are hydraulically connected in series. However, these two drives are not mechanically coupled to one another. Because of their different structure and their different mode of operation, namely once with the internal impeller on the outside and once with the external impeller on the outside, and also because of the different embodiment of the Guide channels and the blades have the two drive turbines 18 and 19 but a different operating speed and a different speed behavior depending on the flow rate and the working pressure of the working fluid.
  • the angular velocity of the bearing housing 12 can also be changed by the spray nozzle 61 used on its peripheral surface as a control nozzle.
  • the angular velocity of the spray head 13 can be changed in relation to the normal operating speed of the drive turbine 19, both increased and decreased, in particular in the case of the double spray nozzle 102, by adjusting one of the orifice tubes 62 so that its jet direction is a circumferential component with respect to the Receives axis of rotation 17, in the same direction or in the opposite direction to the rotational movement of the spray head 13.
  • the cleaning device 110 shown in FIGS. 4 and 5 is partly identical or similar to the cleaning device 10 and partly modified compared to the first embodiment. Insofar as components or assemblies are not explained separately below, it can be assumed that they are of the same or at least similar design to the corresponding parts or assemblies of cleaning device 10.
  • the cleaning device 110 has the holder 111, the bearing housing 112 and the spray head 113.
  • the bearing housing 112 is pivotally mounted on the holder 11 by means of the pivot bearing 114.
  • the spray head 113 is rotatably mounted on the bearing housing 112 by means of the rotary bearing 115.
  • the pivot axis 116 of the bearing housing 112 and the axis of rotation 117 of the spray head 113 in turn enclose an angle of at least approximately 135 °.
  • the drive 118 in the form of a drive turbine ensures the rotary movement of the bearing housing 112.
  • the drive 119 also takes the form of a drive turbine for the rotary movement of the spray head 113.
  • the holder 111 has a short rod part 121.
  • the bearing parts of the pivot bearing 114 connected to the holder 111 are in turn arranged at one end thereof.
  • a coupling piece 122 is screwed on.
  • a plug-in sleeve 123 is arranged on the coupling piece 122, generally in a molded manner.
  • This plug-in sleeve 123 has an approximately sleeve shape. It serves to accommodate a guide or holding rod 124.
  • a bayonet lock 125 is provided for the force-locking coupling between the holding rod 124 and the push-in sleeve 123.
  • the slots 127 which are matched to the coupling pin 126 and are arranged in mirror image with respect to the pivot axis 116, are present on the plug-in sleeve 123.
  • the holding rod 124 here has a purely holding and guiding function for the cleaning device 110.
  • a threaded hole 128 is provided on the coupling piece 122 next to the push-in socket 123, into which a hose connector 129 is screwed, which is connected to a supply hose 131 for the working medium is.
  • a plurality of connection channels 132... 134 connect to the threaded hole 128, of which the last connection channel 134 connects to the feed line 135 in the rod part 121 designed as a blind hole.
  • This design of the holder 111 has the advantage that the supply line of the working medium is separated from the holding parts, so that, if necessary, the holding rod 124 can be attached or removed or lengthened or shortened without the supply of the working medium having to be interrupted each time because this is now done via the separate supply hose 131.
  • the pivot bearing 114 is largely identical to the pivot bearing 14. With him, only the bearing pin 136 and the outer bearing plate 137 located below are modified. The blind hole serving as feed line 135 is deeper. In addition to the first group of transverse bores 138 located approximately in the middle cross-sectional plane, there is a second group of transverse bores 139 at a certain axial distance below. In the cross-sectional plane of these transverse bores 139, a circumferential groove 141 is made in the inner circumferential surface of the bearing disk 137. An outlet channel 142 connects to this on one side.
  • the bearing housing 112 is formed by a single circular cylindrical body. One end face is aligned normal to the cylinder axis. Its other end face is inclined at an angle of at least approximately 135 ° with respect to the cylinder axis.
  • the rotary bearing 115 for the spray head 113 is arranged on the latter end face.
  • An annular groove 143 is arranged on the bearing housing 112 in the end face facing the pivot bearing 114. Their mean radius is approximately equal to the mean center distance of the drain channels 144 in the bearing plate 137 below.
  • the annular groove 143 serves as a collecting channel for the working fluid flowing out of the drive turbine 118 through the drain channels 144. This is fed via the connecting channel 145, which is designed only as an axial blind hole, to the spray nozzle 61 acting as a control nozzle on the outside of the bearing housing 112. The spray nozzle 61 is thus hydraulically connected in series with the drive turbine.
  • the pivot bearing 115 is modified compared to the pivot bearing 15.
  • the blind hole 147 in the bearing housing 112 is provided with an internal thread.
  • the bearing pin 151 is screwed into it.
  • the inner bearing disk 152 sits on it.
  • the disk part 153 of the spray head 113 serves here as the one outer bearing disk of the pivot bearing 115.
  • the spacer ring 155 is located in the circular cylindrical interior of the edge bead 154 of the spray head 113. Outside, the second outer bearing disk 156 is arranged .
  • the inner bearing disk 152 is also designed as a stator 158 and the spacer ring 155 as an impeller 159.
  • the working fluid is supplied to the spray head 113 via the feed line 161 designed as an axial blind hole. From this inlet line 161, the working medium passes via two diametrically extending transverse bores 162 into a circumferential groove 163 on the inner circumferential surface in the stator 158. From there it flows through guide channels 164 oriented tangentially to the groove base of the circumferential groove 163 and emerges on the outside of the guide wheel 158 with a tangential component.
  • the blades 165 are arranged, which here have the shape of hollow circular cylinder sections which extend over the entire height of the impeller 159.
  • annular space 167 which is formed by a circumferential groove in the outer circumferential surface of the impeller 159 and in the inner circumferential surface of the edge bead 154 of the spray head 113.
  • the distributor lines 168 for the working medium which are designed here as a diametrically extending through bore of the edge bead 154, adjoin this annular space 167. At their mouths on the outside of the rim 154 these holes are with a Sealing plug, not shown, is closed.
  • Branch lines branch off from the distribution lines 168 in a manner similar to the branch lines 99.
  • the spray nozzle 171 and the spray nozzle 172 are connected to it, which are designed in the same way as the spray nozzles 101 and 102, respectively.
  • the driving turbine 119 is connected in parallel to the driving turbine 118.
  • the speeds of the two drive turbines 118 and 119 can be set to the desired ratio to one another.
  • the hollow screw for the control nozzle 61 is not designed like the hollow screw 103 but like the hollow screw 64, which is provided with a threaded pin 68 and with a conical tip 69.
  • the passage cross section to the control nozzle 61 and thus the passage cross section of the drive turbine 118 can be changed and thus the flow rate of the working medium in the drive turbine 118 can be increased or decreased, which results in an opposite change in the flow rate for the drive turbine 119.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Nozzles (AREA)
  • Spray Control Apparatus (AREA)
EP87107444A 1986-05-26 1987-05-22 Dispositif de nettoyage pour réservoirs et similaires Withdrawn EP0247532A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3617783 1986-05-26
DE19863617783 DE3617783A1 (de) 1986-05-26 1986-05-26 Reinigungsvorrichtung fuer behaelter und dergleichen

Publications (2)

Publication Number Publication Date
EP0247532A2 true EP0247532A2 (fr) 1987-12-02
EP0247532A3 EP0247532A3 (fr) 1988-11-09

Family

ID=6301715

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87107444A Withdrawn EP0247532A3 (fr) 1986-05-26 1987-05-22 Dispositif de nettoyage pour réservoirs et similaires

Country Status (2)

Country Link
EP (1) EP0247532A3 (fr)
DE (1) DE3617783A1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006048067A1 (fr) * 2004-11-02 2006-05-11 Tuchenhagen Gmbh Dispositif de nettoyage de recipient
WO2007090395A1 (fr) * 2006-02-08 2007-08-16 Alfa Laval Tank Equipment A/S Ensemble de nettoyage
WO2017028831A1 (fr) * 2015-08-17 2017-02-23 Netzsch-Feinmahltechnik Gmbh Dispositif de lavage et installation de traitement de produit

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19938435C2 (de) * 1999-08-13 2002-02-28 Walter Geraetebau Gmbh Reinigungsvorrichtung
DE102021006330A1 (de) * 2021-12-23 2023-06-29 Gea Tuchenhagen Gmbh Reiniger

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1051189A (fr) * 1900-01-01
US1857766A (en) * 1928-08-08 1932-05-10 Joseph V Palmer Tank cleaning device
US2969188A (en) * 1956-06-05 1961-01-24 Lamy D Etudes Et De Rech S Sol Apparatus for cleaning tank-waggons, tanks and other chambers

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1112936A (en) * 1965-10-27 1968-05-08 Cp Equipment Ltd Improvements in or relating to tank cleaning apparatus
DE7538187U (de) * 1975-11-29 1976-04-01 Fa. Alfred Kaercher, 7057 Winnenden Fassreinigungsgeraet

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1051189A (fr) * 1900-01-01
US1857766A (en) * 1928-08-08 1932-05-10 Joseph V Palmer Tank cleaning device
US2969188A (en) * 1956-06-05 1961-01-24 Lamy D Etudes Et De Rech S Sol Apparatus for cleaning tank-waggons, tanks and other chambers

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006048067A1 (fr) * 2004-11-02 2006-05-11 Tuchenhagen Gmbh Dispositif de nettoyage de recipient
EP2620226A1 (fr) * 2004-11-02 2013-07-31 GEA Tuchenhagen GmbH Dispositif de nettoyage de récipient
WO2007090395A1 (fr) * 2006-02-08 2007-08-16 Alfa Laval Tank Equipment A/S Ensemble de nettoyage
CN101378852B (zh) * 2006-02-08 2010-08-04 阿尔法拉瓦尔容器装备股份有限公司 清洁装置
US8177917B2 (en) 2006-02-08 2012-05-15 Alfa Laval Tank Equipment A/S Cleaning assembly
WO2017028831A1 (fr) * 2015-08-17 2017-02-23 Netzsch-Feinmahltechnik Gmbh Dispositif de lavage et installation de traitement de produit

Also Published As

Publication number Publication date
DE3617783A1 (de) 1987-12-03
EP0247532A3 (fr) 1988-11-09
DE3617783C2 (fr) 1988-12-29

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