EP2277634A1 - Cleaning device for cleaning conduits - Google Patents

Abstract

The device (1) has a motor (2) and three rolls that are arranged on a circumference of a spring shaft (6). Axes of two of the rolls are firmly aligned so that the axes along with opposite transport force acts on the spring shaft. An axis of the third roll is adjustable in a spatial position such that the transport force of the third roll assists the transport forces of the other rolls. A handle tube (8) movably encloses the spring shaft and includes an adjusting part for adjusting the third roll in the transport direction of the spring shaft.

Description

The starting position - state of the art:

The invention relates to a hand-held cleaning device for cleaning pipelines by means of a spring shaft, equipped with a motor, a drum for receiving and outputting the spring shaft and a transmission housing in which a plurality of radially acting on the spring shaft rollers are arranged with axes, the are aligned with radial distances at angles to the axis of the spring shaft.

The problem:

The need for pipe cleaning increases with the likelihood of clogging pipes. There are a variety of causes, such as blockages through paper such as toilet paper, handkerchiefs, napkins u. Like., Disposed accidentally diapers and washcloths, deposits due to calcification, entrained binders, paint residues, kitchen waste, penetrated by connecting and breaking points plant roots, rainwater entrained impurities, cross-sectional changes and branching of the pipeline, etc. The effects may also be additive and cumulative reinforce until dense constipation. Particularly dangerous are, for example, through joints and putties penetrated plant roots, where just about everything gets stuck, which is not very thin. Some plant roots work their way through to watering holes.

Accordingly diverse are the cleaning tools that can be attached to the spring shafts via appropriate couplings. These include cutting heads, club drills, return drills, hopper drills, crosshead drills, blade head drills, carbide drills, sawtooth cutting heads, root cutters, fork heads, grease drippers, chain spinner heads with and without spikes, carbide heads, etc.

The necessary manipulations are correspondingly varied: rapid or slow continuous advancement and retraction of the cleaning tools, drilling, scraping or sawing "on the spot" or oscillating with reciprocating movements of the tools against obstinate blockages and when retrieving partial portions of the blockage. In this case, e.g. not the torsional strength of the spring shaft are exceeded. Furthermore, in hand machines, a reliable attitude without promotion of fatigue must be possible, especially centric with respect to introduction openings in the pipeline.

In the field of pipe cleaning machines, helical shafts were originally used in steel wire - also known as "cleaning spirals" in industry jargon - in which the individual windings were at a distance from each other. Thus, it was possible that the spring waves "screwed" by thread action in the pipes only by their torque and also returned after reversing the direction of rotation. For this reason, even radially acting friction clutches in suitcase-shaped portable or mobile drive machines were sufficient.

It has also been used positively working drive units in which hooks, claws, balls or other projections intervened in the spaces between the turns. In the above cases, however, a reversal of the transport direction of the spring shaft was only possible by reversing its direction of rotation. In machines with a drum for receiving the spring shaft, however, this would be associated with disadvantages: The mass of drum and spring shaft generated during braking and restarting considerable moment of inertia, the Dismantling is time consuming and burden the operator.

With the transition to spring waves without significant winding spacing is therefore transferred to drives with radially pressed rollers whose outer surfaces are at least substantially cylindrical surfaces. As soon as the axes of such rollers - correspondingly offset radially - are at an acute angle to the axis of the spring shaft, friction forces and corresponding force parallelograms to the spring shaft axially parallel transport forces are generated, which lead depending on the spatial position of the angular position to a different strong feed or retraction of the spring shaft , Depending on the size of the radial contact forces of the rollers, considerable feed forces can be generated.

If the axes of the rollers are parallel to the axis of the spring shaft, there is a standstill of the spring shaft in its axial direction, but with continued rotation, which is determined in the same sense of rotation (!) By the drum and its drive. This enables lightning-fast switching of the direction of rotation without any notable external release of force. In particular, the feed or retraction of the spring shaft is thereby decoupled from the pitch of the turns of the spring shaft. This is also the kinematic basis of the invention.

Prior art documents:

By the DE 30 05 724 C2 and the corresponding one US 4,218,802 as well as through the US 3,691,583 it is known in pipe cleaning machines for manual operation, rotatably to provide a motor-driven drum with a coaxial hollow shaft on which a rotatable hand-adjustable handle tube with a funnel-shaped widened end is stored as a hand guard. By axial movement of the handle tube locking body can be pressed in the form of balls or pins by means of an inner conical surface radially into the interstices of the spring shaft to force their advance. In a retraction of the detent body of the feed is interrupted, the spring wave, which is referred to as "snake" (snake), but further rotated. The feed rate is changed by controlling the engine speed. A motor retreat The spring shaft is only possible by reversing the direction of rotation of the drum. For this sees the US 3,691,583 a toggle switch on the engine.
Otherwise, the spring shaft must be pushed back into the drum by hand. A further development, in which the locking body are replaced by easily replaceable leaf springs and the withdrawal of the spring wave can be effected by reversing the direction of rotation of the engine is in the EP 407 327 B1 or their translation DE 690 00 316 T2 disclosed. As far as it is the control of the transport of the spring shaft by a relative to the drum sliding handle tube, this is the closest Kommerte state of the art.

By the EP 0 894 906 B1 and the corresponding one US 5,901,401 It is known to arrange for the advance of a spring shaft on its periphery a single group of three rollers with smooth surfaces, two of which are mounted with fixed axial positions in the end of a housing and the third guided radially movable in a radial bore and therein by the pairing a cylindrical pin and a radial groove is secured against rotation. By a projecting actuating lever, this third roller can be pressed to different degrees on the spring shaft or released by relieving a spring. However, this can only be effected in one direction, which depends on the speed of the spring shaft and the constant and identical inclination of the rollers, which is indicated at 30 degrees to the axis of the spring shaft. A thrust reverser with the same direction of rotation is not possible with this arrangement, possibly a standstill by withdrawal of the third roller. Again, a withdrawal of the spring wave in the drum only with a reversal of the direction of rotation of the drum and thus time-consuming possible.

By the US 6,243,905 B1 Various embodiments of pipe cleaning machines are known in which the drum with the spring shaft and the motor are arranged on a frame, so that stand-up devices result that can not be performed by hand. In one of the cases, the feed device is mounted at a distance from the drum on the frame ( Fig. 5 and 6 ), in another case at the end of a hose, which in turn is connected to the frame via a coupling is ( Fig. 7 till 9). The feed device has three free-running rollers whose cylindrical surfaces touch the spring shaft and their axes of rotation are evenly distributed on the circumference and arranged obliquely in the same direction so that the rotation of the spring shaft rotation of the rollers and this rotation in turn generates the advance of the spring shaft. It is also possible to describe the spatial position of the axes of the rollers such that these axes are tangents to a cylindrical surface which surrounds the spring shaft with the distance of the roller radius and in each case run obliquely to a surface line of the cylindrical surface. Due to these spatial positions and the overlapping of the movements, the rollers have the effect of driving rollers. To turn on and off one of the three rollers is mounted radially movable on the inside of an angle lever. A changeover of the transport direction of the spring shaft from extension to retraction is possible here exclusively by switching the direction of rotation of the spring shaft. For this purpose, the drum, can be stored in the different lengths of the spring shaft, stopped and restarted in the opposite direction. This is time-consuming because of the inertia of the system and hinders the elimination of blockages by rapid alternating switching of the direction of rotation. If a cleaning tool is arranged at the free end of the spring shaft, which receives impurities by a helical movement, they would be released in a reversal of the direction of rotation and remain in the pipeline. As far as the arrangement of three rollers is concerned, this prior art may be referred to as the closest one.

By the DE 690 32 169 T2 and the US 6,360,397 B1 it is known in pipe cleaning machines with chassis, each switching a single group of three distributed on the circumference of the spring shaft rollers for reversing the same direction and synchronously. In the DE 690 32 169 T2 This is done by the rollers are arranged by means of cylindrical bearing blocks in radial holes of a holder and to these bore axes have radial pins which engage in radial slots of a circular plate. By pivoting this plate by means of a protruding hand lever then the thrust reversal is effected. In the US 6,360,397 B1 The thrust reversal happens by the whale center is mounted on three axes in and between two walls of a telescopic capsule. These walls are pivotable relative to each other by means of a radially projecting lever, so that the rollers are in turn reversed in the same direction and synchronously about virtual and radial axes for thrust reversal. However, this requires a total of six precise joints at the ends of all axes, so that these devices require a high production and maintenance costs. It should be noted that the spring wave during retraction also entrains impurities that exert a disturbing influence on all fine mechanical components. In both cases, the grasping with one hand only because of the fact that the complete equipment each have a chassis, and thus are not hand-held devices.

By the US Pat. No. 6,665,228 B1 It is known to arrange a total of five rollers for the purpose of thrust reversal of the spring shaft in a housing, all of which are mounted in bearing blocks with cylindrical enveloping surfaces. Of these four are arranged at fixed angles in the housing, in each case two for the one of the two transport directions and the other two for the transport direction opposite thereto. The fifth roller is pivotally mounted on a turntable with a diametrical lever and can be brought by this alternatively with two of the fixed rollers in an interaction in which then three axes - seen in the circumferential direction - at the same angle to the axis of the spring shaft are aligned. Although the device does not require reversal of the direction of rotation of the drum and spring shaft, but because of the many fits consuming in the production and has a long extension. Most importantly, to reverse thrust, the operator must move one hand around the turntable for a large pivotal path, while the weight of the cleaning machine must be picked up by the other hand.

By the WO 2006/112848 A1 and the US 2005/0246846 A1 It is known to arrange at each end of a device for reversing the direction of transport of spring waves, each a group of three rollers, of which the axes of each group, distributed on the circumference of the spring shaft, are aligned with the same direction of transport, but both groups have opposite transport directions. Since in each case only one of these groups can be used simultaneously, two of the rollers of each group are each arranged on a double-armed, radially projecting angle lever, which may be formed in one or two parts. The axes of each group of rollers are aligned in the same direction and at an acute angle to the axis of the spring shaft ("snake"), and the thrust direction of the spring shaft can be reversed without changing the direction of rotation of the drum and spring shaft. The thrust reverser is carried out either by a one-piece, centrally mounted rocker with two lever arms or by two oppositely projecting levers which are pivotable about a common axis which extends transversely to the spring shaft. The device is arranged at the end of a guide tube for the spring shaft, so that it can not be actuated by a push handle, which is mounted on an axle fixed hollow shaft of a motor-driven drum and also for manual mounting of the machine.

The task:

The invention is based on the object to provide a cleaning device of the type described above, which manages with a smaller number of precision parts, a metered transport speed of the spring shaft in both axial directions and a fast switching of the transport direction of the spring shaft without reversing the direction of rotation of the drum allowed, without that in this case a displacement of a hand of the operator would have to be done on a protruding movable lever, while reducing the risk of fatigue for the operator despite the manual operation is reduced.

The solution of the problem by the invention:

1. a) eine einzige Gruppe von drei auf den Umfang der Federwelle verteilten Walzen, von denen die Achsen zweier Walzen lagefest so ausgerichtet sind, dass diese mit entgegengesetzten Transportkräften auf die Federwelle einwirken, und dass die Achse der dritten Walze in ihrer Raumlage derart verstellbar ist, dass die Transportkraft der verstellbaren Walze wahlweise die Transportkraft der einen lagefesten Walze oder der anderen lagefesten Walze unterstützt, und
2. b) durch ein die Federwelle verschiebbar umschliessendes Griffrohr mit Mitteln für die Verstellung der dritten Walze in beide Transportrichtungen der Federwelle.

The above object is achieved according to the invention by:

1. a) a single group of three rollers distributed on the circumference of the spring shaft, of which the axes of two rollers are positionally aligned so that they act with opposite transport forces on the spring shaft, and that the axis of the third roller is adjustable in its spatial position, that the transport power of adjustable roller supports either the transport force of a position-fixed roller or the other positionally stable roller, and
2. b) by a spring shaft slidably enclosing handle tube with means for adjusting the third roller in both directions of transport of the spring shaft.

The advantages of the invention:

By the invention wurd said object was fully achieved, and it is a cleaning device of the type described above improved by the fact that it requires a smaller number of precision parts, a metered transport speed of the spring shaft in both axial directions and a fast switching of the transport direction of the spring shaft Without reversing the direction of rotation of the drum allows, without this a displacement of a hand of the operator would have to be done on a protruding movable lever, while reducing the risk of fatigue for the operator despite the manual operation is reduced. The invention is based on the surprising finding that the task can be achieved with only three rollers, of which only one is adjustable.

Further developments of the invention:

• * das Getriebegehäuse am Ende eines mit der Trommel verbundenen Stützrohres angeordnet ist, wenn in das Getriebegehäuse ein Umschaltmechanismus hineinragt, an dessen innerem Ende ein Lagerbock mit der verstellbaren Walze angeordnet ist, wenn der Lagerbock um eine zur Federwelle senkrecht stehende Schwenkachse schwenkbar ist und wenn das Griffrohr auf dem Stützrohr verschiebbar angeordnet ist,
• * der Lagerbock mit der Walze in radialer Richtung gegenüber den beiden ortsfesten Walzen verstellbar ist,
• * der Lagerbock mit einem Zahnsektor versehen ist, der in eine Zahnreihe eingreift, die duch das Griffrohr verschiebbar ist,

• * die Zahnreihe an der Innenwand einer Kammer angeordnet ist, die koaxial mit dem Griffrohr verbunden ist und einen grösseren Innendurchmesser aufweist als der Aussendurchmesser des Griffrohres,
• * das Getriebegehäuse in die Kammer eingesetzt ist, wenn die Kammer eine Ausnehmung und das Getriebegehäuse eine Ausnehmung besitzen, die in montiertem Zustand eine radiale Passage bilden, durch die der Umschaltmechanismus in radialer Richtung eingeführt und sein Zahnsektor mit der Zahnreihe gekoppelt werden kann,
• * am Ende des Stützrohres ein Käfig angeordnet ist, der zwei radiale Kreisscheiben und mehrere achsparallele Stege besitzt, die das Getriebegehäuse einschliessen,
• * das Getriebegehäuse auf seiner Aussenseite achsparallele Nuten besitzt, in die die Stege formschlüssig eingreifen,
• * der Umschaltmechanismus ein Zwischengehäuse mit zwei Ausnehmungen besitzt, wenn in die äussere Ausnehmung die Nabe eines Einstellknopfes hineinragt und wenn in der anderen Ausnehmung der Lagerbock mit seinem Zapfen drehbeweglich gelagert ist,
• * zwischen dem Einstellknopf und dem Lagerbock ein elastisches Element zur Einstellung der Anpresskraft der Walze gegenüber den ortsfesten Walzen angeordnet ist,
• * das Zwischengehäuse eine Flanschplatte aufweist, mittels welcher es mit dem Getriebegehäuse verbindbar ist,
• * die Flanschplatte in der Ausnehmung des Getriebegehäuses befestigbar ist,
• * die Kammer gegen Verdrehen formschlüssig mit dem Getriebegehäuse verbunden ist,
• * die formschüssige Verbindung mittels mindestens einer Sicke in der Wand der Kammer und mindestens einer Nut auf dem Umfang des Getriebegehäuses ausgeführt ist,
• * das Stützrohr auf seinem Aussenumfang und gegenüber dem Griffrohr mit Nuten zur Aufnahme von Schmutz versehen ist, und/oder, wenn
• * die Raumlagen der Zahnreihe und des Zahnsektors so gewählt sind, dass die Bewegungsrichtungen des Handgriffs und der Trommel mit den Transportrichtungen der Federwelle übereinstimmen.

It is particularly advantageous in the course of further embodiments of the invention if, either individually or in combination:

• * The transmission housing is arranged at the end of a drum connected to the support tube when in the transmission housing protrudes a switching mechanism, at the inner end of a bearing block with the adjustable roller is arranged, when the bearing block is pivotable about a spring shaft perpendicular to the pivot axis and if Handle tube is slidably disposed on the support tube,
• the bearing block with the roller is adjustable in the radial direction with respect to the two stationary rollers,
• * The bearing block is provided with a tooth sector, which in one Tooth row engaged, which is displaceable by the handle tube,

• * the row of teeth is arranged on the inner wall of a chamber, which is coaxially connected to the handle tube and has a larger inner diameter than the outer diameter of the handle tube,
• the gear housing is inserted into the chamber when the chamber has a recess and the gear housing has a recess which, when assembled, forms a radial passage through which the switching mechanism can be introduced in the radial direction and its tooth sector can be coupled to the row of teeth;
• * At the end of the support tube, a cage is arranged, which has two radial discs and a plurality of axially parallel webs, which enclose the gear housing,
• * has the gear housing on its outer side axially parallel grooves into which the webs engage positively,
• * The switching mechanism has an intermediate housing with two recesses, when the hub of an adjusting knob protrudes into the outer recess and when the bearing block is rotatably mounted with its pin in the other recess,
• * between the adjusting knob and the bearing block is arranged an elastic element for adjusting the pressing force of the roller relative to the stationary rollers,
• * the intermediate housing has a flange plate, by means of which it is connectable to the transmission housing,
• the flange plate can be fastened in the recess of the transmission housing,
• * the chamber is positively connected to the transmission housing against rotation,
• * the positive connection is made by means of at least one bead in the wall of the chamber and at least one groove on the circumference of the gear housing,
• * The support tube is provided on its outer circumference and opposite the handle tube with grooves for receiving dirt, and / or, if
• * The spatial positions of the row of teeth and the toothed sector are chosen so that the directions of movement of the handle and the drum coincide with the transport directions of the spring shaft.

The detailed description:

An embodiment of the subject invention and its modes of action and other advantages will be described below with reference to the FIGS. 1 to 7 explained in more detail.

Figur 1

eine perspektivische Aussenansicht in Verbindung mit Funktionsdiagrammen,

Figur 2

eine Explosionsdarstellung funktionswesentlicher Teile,

Figur 3

eine weitere Explosionsdarstellung zur Erläuterung des Zusammenwirkens der drei Walzen,

Figur 4

eine weitere Explosionsdarstellung des Zusammenwirkens des Zahntriebs zwischen Griffrohr und Schwenkrolle in einer über- Kopf-Darstellung gegenüber Figur 3,

Figur 5

einen vereinfachten axialen Einblick in das Ende des Griffrohres zur Erläuterung des Zusammenwirkens der drei Walzen,

Figur 6

eine Draufsicht auf die Walzengruppe senkrecht zur Federwelle bei Ausführung eines Vorschubs, und

Figur 7

eine Draufsicht auf die Walzengruppe senkrecht zur Federwelle bei Ausführung eines Rückzugs.

Show it:

FIG. 1

an external perspective view in connection with function diagrams,

FIG. 2

an exploded view of functionally essential parts,

FIG. 3

a further exploded view for explaining the interaction of the three rollers,

FIG. 4

a further exploded view of the interaction of the pinion between the handle tube and caster in an overhead view opposite FIG. 3 .

FIG. 5

a simplified axial view into the end of the handle tube to explain the interaction of the three rollers,

FIG. 6

a plan view of the roll group perpendicular to the spring shaft when performing a feed, and

FIG. 7

a plan view of the roller group perpendicular to the spring shaft in execution of a withdrawal.

In FIG. 1 a complete cleaning device 1 is shown, to which a motor 2 with a handle 3 and a switch 4 belong, as is also known from hand drills ago. To the motor, a rotatable drum 5 is attached for receiving a spring shaft 6. The drum 5 has a fixed attached guide tube 7 ( FIG. 2 ), which is coaxially surrounded by a handle tube 8, which is provided in the direction of the drum 5 with a funnel-shaped hand guard 9. This hand guard 9 partially covers the likewise funnel-shaped end wall 5a of the drum 5. The handle tube 8 merges into a cylindrical chamber 10, in which the complete adjusting mechanism for the movement of the spring shaft 6 is housed. An adjusting knob 11 is used to set a pressing force of the adjustable roller to the two stationary rollers, which will be explained in more detail below.

In FIG. 1 in each case only the end of this spring shaft 6 is shown, and at the local thickening it can be seen that this end already has a tool function. The top right box shows the options for the direction of rotation of the motor shaft, and "R" stands for clockwise rotation and "L" for counterclockwise rotation. This switching is not mandatory for the main function of the invention, but increases the flexibility of the device. The terms "clockwise rotation" and "counterclockwise rotation" refer to the viewing direction of the operator, ie to the viewing direction via the drum 5 to the working tool at the end of the spring shaft 6. The same applies to the course of the winding of the spring shaft 6.

In the box below the settings are shown by means of the handle tube 8. The left half of the box explains the processes for a clockwise rotation "R" of the spring shaft 6. In the middle of the handle tube 8 is in a neutral position, indicated by a "0". The axis of the adjustable roller is parallel to the axis of the spring shaft 6 ( FIG. 5 ), so that no axial movement of the same takes place. If the handle tube 8 and the drum 5 are pushed together (upper illustration), the spring shaft 6 is advanced. If the handle tube 8 and the drum 5 are pulled apart (lower illustration), the spring shaft 6 retracts Operations for a left turn "L" of the spring shaft 6. In the middle of the handle tube 8 is in a neutral position, indicated by a "0". The axis of the adjustable roller is parallel to the axis of the spring shaft 6 (again FIG. 5 ), so that no axial movement of the same takes place. If the handle tube 8 and the drum 5 are pushed together (upper illustration), the spring shaft 6 is withdrawn. If the handle tube 8 and the drum 5 are pulled apart (lower illustration), the spring shaft 6 is advanced.

The lower left box explains the function of the adjustment knob 11: By the clockwise rotation in the direction of arrow "+" is an amplification of the contact pressure of the adjustable roller to the two stationary rollers. By turning it to the left in the direction of the arrow "-", the contact force of the adjustable roller is reduced to the two stationary rollers. All these functions will be explained in detail below in connection with the remaining figures, in which the previous reference numerals are retained.

The FIG. 2 shows a support tube 12 with grooves 12 a, which is arranged in the assembled state between the guide tube 7 and the handle tube 8. The grooves 12a are intended to intercept about entrained by the spring shaft 6 during retraction impurities to avoid binding of the handle tube 8. The support tube 12 terminates in a concentric circular disc 13, emanating from the three axially parallel and equidistant webs 14. These webs 14 serve to receive a high-strength gear housing 15, which has three grooves 16 on the circumference, which are formed according to cross section and spatial distribution complementary to the webs 14. The transmission housing 15 has a cavity 17 whose shape and purpose will be explained in more detail below. In mirror-symmetrical arrangement and training to the circular disc 13 with the webs 14 is in the viewing direction in front of the transmission housing 15 yet another circular disc 18 arranged with three webs 19. By screwing the circular discs 13 and 18 via the webs 14 and 19 thus creates a cage in which the gear housing 15 is mounted immovably. The switching mechanism 20 will be described with reference to FIGS FIGS. 3 to 5 explained in more detail.

According to FIG. 3 The switching mechanism 20, viewed from the outside inwardly, the aforementioned knob 11, an intermediate housing 21 with two recesses 21 a and 21 b, of which one 21a for the hub 11a of the knob 11 and the other 21 b for receiving a Bearing blocks 22 with the movable roller 23 is used. For the purpose of centering and guiding the bearing block 22 has a pin 22 a, which is surrounded by a spring assembly, not shown here. As a result, by means of the adjusting knob 11, the contact pressure to the other two, fixedly mounted rollers 24 and 25 regulate. These are introduced in the direction of the two arrows in the cavity 17 of the gear housing 15 and mounted there by means not shown screws on inclined surfaces, followed by the spatial course even more detailed versions.

For the purpose of a linear and paraxial, but rotationally fixed displacement of the handle tube 8 with the attached or molded-in chamber 10, the latter is provided with an axially parallel bead 10a, which engages in a complementary groove 26 of the gear housing 15.

The Figures 3 and 4 show an essential feature of the invention: The chamber 10 has in its cylindrical wall a recess 27, one edge region of which is accompanied by an axis-parallel row of teeth 28. Likewise, the transmission housing 15 is provided with a radial recess 29. Once the transmission housing 15 is housed in the chamber 10, the recesses 27 and 29 form a passage through which the switching mechanism 20 can be inserted radially. In this case, a tooth sector 30, which is connected to the bearing block 22, in engagement with the row of teeth 28, so that by the displacement of the handle tube 8, those movements can be performed, based on the FIG. 1 have been described. It turns the bearing block 22 about its pin 22a.

The FIG. 5 shows a longitudinal axis "AL", which is also the system axis and the axis of the spring shaft 6 and which determines the viewing direction here. In accordance with the FIGS. 6 and 7 On the circumference of the spring shaft, the rollers 23, 24 and 25 are arranged with their axes A1, A2 and A3. The rollers 24 and 25 are spatially fixed with their inner bearing rings by screwing on not visible here oblique surfaces within the gear housing 15. The spatial position has been chosen so that their axes A2 and A3 intersect in a virtual point "P", but at the same time run obliquely and tangentially to a virtual cylindrical surface, which concentrically surrounds the axis "AL" with a corresponding distance. As a result, the rollers 24 and 25 are arranged mirror-symmetrically to each other, and rotate, driven by the contact with the spring shaft 6, in opposite directions of rotation. This results in frictional forces, one component of which runs parallel to the axis "AL." These components extend in opposite directions, and thus do not generate any axial movements of the spring shaft 6 due to a force equilibrium.

This is where the control effect according to the invention sets in which, with the assistance of the FIGS. 6 and 7 is explained: The system now has a further axis, namely the control axis "AS-AS", which also passes through the pin 22a of the bearing block 22 and also the axis "A1" of the roller 23 intersects. In the position shown, the axes "AL" and "A1" run parallel to each other, so that the balance of forces is not disturbed. However, this state changes as soon as the bearing block 22 with the roller 23 is pivoted about the axis "AS-AS". With increasing pivot angle, the roller 23 supports either the transport direction and action of the roller 24 or the roller 25. This applies to both pivoting directions from the position of FIG. 5 out. This support is maximized as soon as the directions of rotation of two rolls, either 23 + 24 or 23 + 25, coincide. The thrust effect of the other roller is thereby overridden or overcome in the result. This effect has been surprisingly confirmed by experiments and leads in connection with the handle tube 8 without grasping the one Hand to a very simple, short, inexpensive and reliable construction and operation with extremely quickly to be accomplished thrust reversal of the spring shaft 6 and without far-reaching components.

The basis of FIG. 5 already explained geometric and kinematic relationships are based on the FIGS. 6 and 7 further explained, which show a top view from above in the direction of the pivot axis "AS-AS", but these figures are even more abstracted. The spatial positions of the two stationary installed rollers 24 and 25 relative to the spring shaft 6, which is driven by clockwise rotation, are unchanged. The pivotable roller 23 is shown in its two end positions, by an angle "α" of, for example, about 20 degrees, in each case about the pivot axis "AS-AS", starting from the central position FIG. 5 , twisted ..

In FIG. 6 The relative positions of the rollers 23 and 24 coincide in the circumferential direction so that they rotate with counterclockwise rotation. This results in the contact points with the spring shaft 6 force components in the direction of the thick arrow, so that the spring shaft 6 is also pushed in the direction of this arrow in a pipe. The opposite force component of the co-rotating roller 25 is overcome.

In FIG. 7 The relative positions of the rollers 23 and 25 coincide in the circumferential direction, so that they also rotate with counterclockwise rotation. This results in the contact points with the spring shaft 6 force components in the direction of the reverse thick arrow, so that the spring shaft 6 is retracted in the direction of this arrow in the drum 5. The opposite force component of the co-rotating roller 24 is overcome.

All this is done exclusively by axial relative movement of the handle 3 and drum 5 on the one hand and handle tube 8 on the other hand, as already in connection with FIG. 1 explained. In this case, the spatial position of the teeth 28/30 is chosen so that the movement directions of the handle 3 and the drum 5 to facilitate the operation the handle tube 8 coincides with the transport directions of the spring shaft 6.

LIST OF REFERENCE NUMBERS

1

cleaner

2

engine

3

handle

4

switch

5

drum

5a

Stinrnwand

6

spring shaft

7

guide tube

8th

handle tube

9

hand protection

10

chamber

10a

Beading

11

adjustment

11a

hub

12

support tube

12a

groove

13

disc

14

Stege

15

gearbox

16

groove

17

cavity

18

disc

19

Stege

20

switching mechanism

21

intermediate housing

21a

recess

21b

recess

21c

flange

22

bearing block

22a

spigot

23

roller

24

roller

25

roller

26

groove

27

recess

28

teeth

29

recess

30

toothed sector

"AL-AL"

longitudinal axis

"AS-AS"

swivel axis

A1

axis

A2

axis

A3

axis

"Α"

angle

"L"

turn left

"P"

Point

"R"

right turn

"0"

neutral position

Claims (16)

Hand - operated cleaning device (1) for cleaning pipelines by means of a spring shaft (6) equipped with a motor (2), a drum (5) for receiving and outputting the spring shaft (6) and with a transmission housing (15) in which a plurality of rollers (23, 24, 25) acting radially on the spring shaft (6) are arranged with axes (A1, A2, A3) aligned with radial distances at angles to the axis of the spring shaft (6),
marked by a) a single group of three on the circumference of the spring shaft (6) distributed rollers (23, 24, 25), of which the axes (A2, A3) of two rollers (24, 25) are positionally aligned so that they are opposite Transport forces on the spring shaft (6) act, and that the axis (A1) of the third roller (23) in its spatial position is adjustable so that the transport force of the adjustable roller (23) optionally the transport force of a positionally fixed roller (24) or the Supported other roll (25), and b) by a spring shaft (6) slidably enclosing handle tube (8) with means for adjusting the third roller (23) in both directions of transport of the spring shaft (6). Cleaning device according to claim 1, characterized in that the gear housing (15) at the end of the drum (5) connected to the support tube (12) is arranged, that in the gear housing (15) protrudes a switching mechanism (20) at the inner end of a Bearing (22) with the adjustable roller (23) is arranged, that the bearing block (22) about a spring shaft (6) perpendicular pivot axis ("AS-AS") is pivotable and that the handle tube (8) on the support tube (8). 12) is arranged displaceably. Cleaning device according to claim 2, characterized in that the bearing block (22) with the roller (23) in the radial direction relative to the two stationary rollers (24, 25) is adjustable. Cleaning device according to claim 2, characterized in that the bearing block (22) with a tooth sector (30) is provided which engages in a row of teeth (28) which is displaceable by the handle tube (8). Cleaning device according to claim 4, characterized in that the row of teeth (28) on the inner wall of a chamber (10) is arranged, which is coaxially connected to the handle tube (8) and has a larger inner diameter than the outer diameter of the handle tube (8). Cleaning device according to claim 5, characterized in that the gear housing (15) is inserted into the chamber (10), that the chamber (10) has a recess (27) and the gear housing (15) has a recess (29) mounted in the Form a radial passage through which the switching mechanism (20) introduced in the radial direction and its tooth sector (30) with the row of teeth (28) can be coupled. Cleaning device according to claim 2, characterized in that at the end of the support tube (12) a cage is arranged, which has two radial circular discs (13, 18) and a plurality of axially parallel webs (14, 19) which enclose the transmission housing (15). Cleaning device according to claim 7, characterized in that the gear housing (15) has on its outer side axially parallel grooves (16) into which the webs (14, 19) engage positively. Cleaning device according to claim 6, characterized in that the switching mechanism (20) has an intermediate housing (21) with two recesses (21a, 21b) that in the outer recess (21a), the hub (11a) of an adjusting knob (11) protrudes and that in the other recess of the bearing block (22) is rotatably mounted with its pin (22a). Cleaning device according to claim 9, characterized in that between the adjusting knob (11) and the bearing block (22) an elastic element for adjusting the pressing force of the roller (23) relative to the stationary rollers (24, 25) is arranged. Cleaning device according to claim 9, characterized in that the intermediate housing (21) has a flange plate (21 c), by means of which it is connectable to the transmission housing (15). Cleaning device according to claim 11, characterized in that the flange plate (21 c) in the recess (29) of the transmission housing (15) can be fastened. Cleaning appliance according to claim 5, characterized in that the chamber (10) is positively connected to the transmission housing (15) against rotation. Cleaning device according to claim 13, characterized in that the positive connection by means of at least one bead (10) in the wall of the chamber (10) and at least one groove (26) on the circumference of the gear housing (15) is executed. Cleaning device according to claim 2, characterized in that the support tube (12) is provided on its outer circumference and opposite the handle tube (8) with grooves (12a) for receiving dirt. Cleaning device according to claim 4, characterized in that the spatial positions of the row of teeth (28) and the toothed sector (30) are selected so that the directions of movement of the handle (3) and the drum (5) with the transport directions of the spring shaft (6) match.

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