EP0362559A2 - Actuating device for a sprinkler or the like - Google Patents

Abstract

In an actuating device (1) for a transportable sprinkler or the like, a water motor (11) has a reducing gear unit (19), whose gear or toothed wheels (41, 42, 43) are located outside the water guide in a separate gear chamber (19) and are therefore dry, the gear chamber (19), however, being integrated into the housing (12) of the water motor (11) in such a way that it is arranged adjacently next to a reversing chamber (23) which serves to guide the water, in which reversing chamber a reversing valve (22) of a reversing device (21) for the alternating reversal of the water motor (11) in both directions of rotation is accommodated. The water motor (11) is input-connected via an output pinion (44) to a carrier (5), a self-engaging overload clutch (77) being arranged in the drive connection. A bypass water guide (86) which works in a pressure-dependent manner and has simple flap valves is additionally provided between the reversing chamber (23) and a rotor chamber (26) which adjoins this axially as well as adjoining the gear chamber (20). Combined with an extremely compact design of the water motor (11) a high functional reliability is thereby produced. <IMAGE>

Description

The invention relates to a drive device for a sprinkler device or the like. According to the invention has a liquid or flow drive, in particular in that at least part of the water to be discharged with the sprinkler device is used to drive at least one movement of the sprinkler device or the like. For this purpose, a liquid guide is provided in a housing, to which a drive rotor is exposed, which possibly performs the desired movement function via a gear, so that advantageous effects result.

If the drive rotor is in the form of a turbine wheel and the gear unit is located within a nozzle housing and within the water supply, the gear unit also runs in a water bath. The gear unit can be mounted on a carrier fastened on a hollow axle directly behind the turbine wheel and within the water-filled housing in engage an inner ring gear that is connected to the housing. This results in a very advantageous irrigation device with the drive device of a reciprocating movement over an infinitely adjustable distance and also an irrigation of almost a rectangular field is possible.

The invention is further based on the object of avoiding disadvantages of known solutions and, in particular, of creating a drive device of the type mentioned which enables a further improved functionality and in particular a particularly compact design.

To solve this problem it is provided in a drive device of the type described above according to the invention that the transmission is shifted substantially out of the water-carrying areas and is preferably arranged in a separate gear chamber, so that its output member, for example an output pinion, without special sealing problems and can therefore be made accessible for the drive intervention in a space-saving manner. In addition, contamination of the gearbox due to water contamination is avoided, and the gearbox runs particularly smoothly with a lubricant or by using self-lubricating materials for the gearwheels.

The transmission is expediently arranged in a transmission chamber which is substantially circular in cross section and which can extend over an arc angle of less than 180 °, so that it takes up very little space. The gear chamber is expediently delimited on the outer circumference by a part of an axially symmetrical or approximately cylindrical housing shell and within this housing shell by, for example, an approximately flat intermediate wall which is approximately parallel to the housing axis, so that the remaining, possibly Larger part of the interior of this housing shell is available for water management. At the end, the gear chamber is closed with transverse walls in which all gear axes can be held and which expediently go over the entire inside width of the housing shell, but are provided with corresponding openings in the area of the water-carrying chamber next to the gear for water passage.

The last-mentioned water-carrying chamber, which lies at least partially essentially in the same longitudinal section of the housing as the gear chamber, can furthermore be used for accommodating further functional parts of the drive device. Preferably, a changeover valve or the like. A changeover device is accommodated within this chamber, by means of which the drive rotor or the output pinion of the transmission can be driven alternately in both directions of rotation in such a way that a changeover element is dependent on the rotation path by the movement generated by the drive device is converted. Said longitudinal section of the housing is thus subdivided into at least one drying chamber separated from the water supply and at least one water-carrying wet chamber, it being possible for appropriate functional parts to be accommodated in each chamber. As a result, as well as by the arrangement of the changeover valve transversely to the housing axis immediately adjacent to the gearbox, not only the length of the water motor, but also its width or diameter can be significantly reduced such that its outer diameter is approximately in the order of its length, namely approximately 50 mm , lies. With this arrangement one above the other, the gearbox could also run in water.

A chamber accommodating the drive rotor expediently closes in the longitudinal direction of the housing directly to the said longitudinal section to the front, ie in the direction of what serdurchflußes, at, this rotor chamber can be separated from the adjacent chambers next to each other by the associated, continuous transverse wall in which the drive rotor is to be stored. The drive rotor is expediently mounted with a very thin shaft which is mounted in a sealed manner in the transverse wall and is in drive engagement with the transmission within the transmission chamber.

In a further embodiment of the invention, the drive rotor arranged axially parallel to the housing is arranged eccentrically with respect to the housing or the rotor chamber lying in the housing axis, its outer diameter being correspondingly smaller compared to the inner width of the rotor chamber. As a result, the rotor axis of the drive rotor can be laid close to the transmission axes on the one hand, and on the other hand, drive nozzles or associated nozzle channels or the associated nozzle channels can be accommodated in a space-saving manner between the region of the housing shell which is further away from the outer periphery of the drive rotor and can be designed with a relatively large cross section.

The axial extent of the rotor chamber need only be slightly larger than that of the drive rotor, while the axial extent of the transverse divided chambers adjoining in the longitudinal direction need only be approximately as large as the associated gear length. In the area of the rotor chamber, the housing can moreover have a smaller outside width than in the area of the gear chamber, so that the end chamber, which closes it, can be overlapped with an annular collar, the outside width of which is equal to that of the housing in the area of the gear chamber. As a result, the water motor can be assembled in a very simple manner as a self-contained structural unit simply by inserting it into an essentially cylindrical receptacle.

The transmission expediently has a very high reduction ratio, so that the drive rotor can be operated at high speed. This reduction ratio and the sealed mounting of the drive rotor mean that the transmission can be essentially self-locking when it is driven from the side of its output pinion. In order to avoid damage in the event of such a force introduction, an overload clutch is expediently provided in the drive connection between the drive rotor and the component in drive engagement with the transmission, for example a carrier, stand or the like is. Advantageously, the overload clutch has coupling members that mesh with one another under pressure in almost any relative position, but the teeth of which can skip one another against the pressure in the event of overload.

For mounting the drive device or the water motor, which expediently pivots with the part to be driven relative to the stator or the like, a shaft is advantageously provided which is detachably but essentially rigidly connected to the housing of the water motor and which swivels relative to the water motor. or rotatable carrier part axially secured against the water motor so that it can be surrounded on its outer circumference by the overload clutch. If this shaft is designed as a hollow shaft, it serves simultaneously for the line connection between a hose connection or the like provided on the carrier and the housing of the water motor. The overload clutch can also be provided in drive devices other than those described.

A particularly advantageous further development, in particular of a drive device of the type described, also results from the fact that the water flow entering the housing of the water motor depends on the flow quantity or of the pressure can be at least partially passed around the drive rotor so that the corresponding partial flow does not act on the drive rotor in the sense of the drive action, although this partial flow is passed through the rotor chamber and is, for example, only prevented from acting on the drive rotor by guide elements. The partial flow is expediently controlled by at least one pressure relief valve between a water-carrying chamber lying to the side of the gear chamber and the rotor chamber, the valve closing part in the form of a simple plate in the rotor chamber being able to be pressed resiliently against a passage opening in such a way that it lifts off when a predetermined pressure is reached and releases the passage bypassing the valve channel or channels. Two valve closing parts are expediently formed by the tongue-like ends of a flat material strip, which is fastened only approximately in the middle between these ends on the associated transverse wall and thereby forms two spring arms projecting in opposite directions and with its ends forms the valve closing parts. This results in a very simple and compact design, especially since the spring arm or springs can be arranged between the valve channels and the rotor axis or between the transverse wall and the opposite end face of the drive rotor at a distance from the rotor axis which is smaller than half the outer diameter of the drive rotor is.

• Fig. 1 eine mit einer erfindungsgemäßen Antriebs­vorrichtung versehene Beregnungsvorrichtung in teilweise geschnittener Ansicht,
• Fig. 2 die Antriebsvorrichtung gemäß Fig. 1 in ver­größerter Darstellung und im wesentlichen im Axialschnitt, jedoch um 90° verdreht,
• Fig. 3 den Wassermotor gemäß Fig. 2 in vergrößerter Darstellung und
• Fig. 4 den Wassermotor gemäß Fig. 3 in Ansicht von links und teilweise geschnittener bzw. aufge­schnittener Darstellung.

These and further features of preferred developments of the invention are evident from the claims and also from the description and the drawings, the individual features being implemented individually or in groups in the form of sub-combinations in one embodiment of the invention and in other fields, and can represent advantageous and protectable versions for which protection is claimed here. An execution Example of the invention is shown in the drawings and is explained in more detail below. The drawings show:

• 1 is a sprinkler device provided with a drive device according to the invention in a partially sectioned view,
• 2 shows the drive device according to FIG. 1 in an enlarged view and essentially in axial section, but rotated by 90 °,
• Fig. 3 shows the water motor of FIG. 2 in an enlarged view and
• Fig. 4 shows the water motor of FIG. 3 in a view from the left and partially cut or cut view.

As shown in FIG. 1 in particular, a drive device 1 according to the invention is provided, for example, for pivoting a sprinkler device 2, which can be set up using a stand 3, an earth anchor or the like. The stand 3 has in the illustrated embodiment two V-shaped downward diverging, extending in the longitudinal direction of the sprinkler, approximately U-shaped stand 4, which are laterally inserted with their ends in two end supports 5, 6 and with these the console or form the fixed or immovable component of the irrigation device 2, on and between which a nozzle housing 7 is mounted as the movable component driven by the drive device. The nozzle housing 7 has on its upper side at least one longitudinal row of differently oriented spray nozzles 8, from which practically one type of water curtain emerges in one plane, which, viewed in the longitudinal direction, swings to the left and / or or is inclined to the right and thus irrigates a base area of adjustable size, for example a lawn or a bed.

The approximately cylindrical housing, which is expanded downward in the area of the drive device 1, has a bearing pin 9 which engages in a bearing opening of the associated carrier 6 at the front end remote from the drive device. The other end of the nozzle housing 7 forming the nozzle carrier is mounted in the associated carrier 5 with a hollow shaft 10 projecting beyond this end. The nozzle housing 7 expediently consists of two lateral half shells made of plastic, which interlock with tongue and groove and are connected to one another in an essentially liquid-tight manner by ultrasonic welding or the like.

The drive device 1 has as the drive motor a fluid-driven motor in the form of a water motor 11, which forms a self-contained structural unit with a housing 12, which essentially lies entirely within the nozzle housing 7 and only has a short rear end section for connecting the transmission to the carrier 5 protrudes from the rear end of the nozzle box 7. The lying housing axis 13 of the water motor 11 coincides with the axis of rotation or pivoting of the nozzle housing 7, the hollow shaft 10 being inserted firmly into the rear end of the housing 11 and being rotatably mounted in the carrier 5 made of plastic. Immediately behind and coaxially with the hollow shaft 10, a connection for a water pipe in the form of a hose connection, preferably a plug-in coupling member of a quick coupling, is inserted into the associated end face of the carrier 5. About the hose connection 14 through the hollow shaft 10, the interior of the housing 12 or the water motor 11 is supplied with pressurized water, which is then fully featured by one at the front end of the housing 11 seen water outlet connection 15 emerges again. On the nozzle-shaped water outlet connection 15 lying in the housing axis 13, an angular pipe bend 16 is plugged with one end sealed, the other end of which is inserted from below into a nozzle line 17 lying inside the nozzle housing 7. This nozzle line 17 extends in the longitudinal direction of the nozzle housing 7 continuously over all spray nozzles 8, such that these are connected directly to the nozzle line 17 with the inner ends of their nozzle bores, the cross sections of which are substantially or several times smaller than those of the nozzle housing 7. The housing 12 of the water motor 11 is inserted directly behind the nozzle line 17 centered in a receptacle 18 of the nozzle housing 7 and secured against rotation, for example, by cams engaging in the rear end wall of the nozzle housing 7. The receptacle 18 can be formed by a plurality of ribs or the like distributed over the circumference, which abut the outer circumference of the housing 12.

In the rear end of the housing 12 of the water motor 11, which is designed as a geared motor, a multi-stage, namely five to ten-stage, preferably eight-stage reduction gear 19 is provided, of which a first gear stage is formed by the input-side drive connection of the gear unit and a further gear stage by the output-side drive connection can be. The gear 19 is provided in a gear chamber 20 of the housing 12, which is separated from the water supply between the hollow shaft 10 and the water outlet connection 15, the length of this gear chamber 20 being less than the outer diameter of the housing 12 in its area.

For alternating switching of the swiveling direction of the nozzle housing 7, a switching device 21 is provided, which is switched by the swiveling movement between two control positions lung operated switch valve 22. This changeover valve 22 is arranged in a changeover chamber 23, which is located in the same longitudinal section of the housing 12 as the gearbox chamber 20, but is connected to the water guide between the hollow shaft 10 and the water outlet connection 15 or directly to the associated end of the hollow shaft 10.

The water flowing through the water guide drives a drive rotor 24 of the hydraulic motor, this drive rotor 24 having a turbine wheel 25 exposed to at least one jet in a rotor chamber 26. This rotor chamber 26 is provided within the housing 12 axially immediately following the gear chamber 20 and the changeover chamber 23. However, the housing 12 has a smaller inner and / or outer diameter in the area of the rotor chamber 26 compared to the area of the gear chamber 20 and the changeover chamber 23. The rotor chamber 26 is supplied directly from the switching chamber 23 with the water flowing through, which then emerges from the rotor chamber 26 directly through the water outlet connection 15.

The housing 12 consists essentially of two housing parts 27, 28 and an end cap 29, which are placed against one another in the axial direction and which are centered against one another by plugging into one another and are connected to one another in a watertight manner by ultrasonic welding or the like. The rear housing part 27 forms the end or end collar passing through the rear end of the nozzle housing 7 and the transmission chamber 20 and the changeover chamber 23 over the largest part of their axial extent. The front housing part 28 is inserted with its rear end, offset in the outer diameter, centered in the front end of the housing part 27, which is complementarily expanded in the inner diameter, and forms at a short distance from the rear housing part 27 an approximately one-piece part of the housing axis 13 which is at right angles to the housing axis Transverse wall 30, which separates the rotor chamber 26 tightly from the gear chamber 20 and spatially from the switching chamber 23. In the rear area, the rear housing part 27 forms an end wall 31, which is formed in one piece with it and over which the aforementioned end collar projects to the rear and which carries the front end of the hollow shaft 10.

The rear housing part 27 furthermore forms an intermediate wall 32 formed in one piece with it, which connects both to the end wall 31 and to the inner circumference of the housing shell of this housing part 27 on opposite sides and, after the front housing part 28 has been attached, also close to the associated side the transverse wall 30 connects. This, for example approximately flat and parallel to an axial plane of the housing intermediate wall 32 is offset from this axial plane approximately by its thickness to the gear 19, so that the gear chamber 20 has a smaller volume than the switching chamber 23. From the end wall 31, a sleeve-shaped water inlet connection 33 protrudes into the housing in one piece with the end wall 31 over part of the height of the intermediate wall 32, this water inlet connection 33 partially penetrating the intermediate wall 32 formed with it, but only in the form of a circular segment in the region of its inner end face is open to the switching chamber 23 and closed to the gear chamber 20. The water inlet connection 33 has an internal thread, into which the hollow shaft 10 is screwed with an external thread provided at its front end in such a way that the end face is braced with respect to the closed part of the inner end of the water inlet connection 33.

The turbine wheel 25 of the drive rotor 24 has a rotor shaft 34, which is inserted into a hub and has a diameter of only about 2 to 3 mm, the end of which projects beyond the rear end face of the turbine wheel 25 through a bearing sleeve 35 sets and is sealed in the bearing opening of this bearing sleeve 35 with an annular seal 36. The, together with the drive rotor 34 and a rotor pinion 37 forming a self-contained assembly sleeve 35, the outer diameter of which is slightly larger than that of the rotor pinion 37, is sealed from the side of the rotor chamber 26 into an opening in the transverse wall 30 so that the rotor pinion 37 protrudes with a part of its circumference into the gear chamber 20 and there establishes the drive connection of the drive rotor 24 with the gear 19. The further away from the turbine wheel 25 on the side of the bearing sleeve 35 and the rotor pinion 37 facing away from this end of the rotor shaft 34 can be mounted in a bearing eye of the transverse wall 30 which projects into the gear chamber 20 and which engages in a corresponding cutout in the intermediate wall 32 and is precisely aligned and additionally supported.

Approximately symmetrically on both sides of an axial plane of the drive conductor 24 or the housing 12 which is approximately at right angles to the intermediate wall 32, the transmission 19 each has a cylindrical pin-shaped transmission axis 39 or 40, each transmission axis having its front end in the housing part 28 or in a blind hole in the transverse wall 30 and is held with its rear end in a blind hole in the housing part 27. A plurality of identical, stepped gear wheels 41, 42, 43 are arranged axially one after the other on each gear axis 39, 40, the gear stage of one gear axis, which is smaller in diameter, drives the gear stage of the other gear axis, which is larger in diameter. The larger diameter gear stage of a first gear 41 of the transmission axis 39 is driven directly by the rotor pinion 37, while a smaller diameter gear stage of the last gear 43 of the same transmission axis 39 forms an output pinion 44 of the transmission 19, the diameter of which compared to the other, smaller gear stages is larger and protrudes through a window 47 over the inner circumference of an inner end collar 46 which is concentric within the end collar 45 engaging in the rear end wall of the nozzle housing 7.

In the area of the output pinion 44, the two end collars 45, 46 are connected to one another via an approximately shell-shaped pinion housing which is formed in one piece with them and which over most of the circumference of the output pinion 44, namely except for the area projecting beyond the window 47 and also at covers the rear end face and forms a bearing extension projecting into a bearing opening of the driven pinion 44, in the blind hole of which the rear end of the gear axis 39 is held. The rear end of the gear axis 40 also extends over part of the axial extent of the front collar 46, the associated region of which is reinforced with a corresponding bearing eye for receiving this rear end.

The outer circumferences of the larger gearwheel stages of the gearwheels 41, 42, 43, which have the same diameter, extend up to close to the associated side of the intermediate wall 32 and close to the inner circumference of the casing of the housing 12 or the gearbox chamber 20, this jacket in the area of the gearbox chamber 20, as can be seen in particular from FIG. 3, is provided on the inner circumference for receiving the gearwheels with a recess in such a way that it is thinner in this area than in the other areas.

To act upon the turbine wheel 35 with a drive water jet, two drive nozzles 48, 49 directed approximately tangentially in opposite directions against the circumference of the turbine wheel 25 are provided, one of which determines the direction of rotation in one direction and the other determines the direction of rotation in the opposite direction. The nozzle openings 48, 49 are located approximately axially parallel to the housing 12 Nozzle channels 50, 51 are connected to the switchover chamber 23, the nozzle channels 50, 51 both projecting freely from the transverse wall 30 into the switchover chamber 23 and projecting forward from the transverse wall 30 approximately up to the end cap 29 into the rotor chamber 26.

The parts of the nozzle channels 50, 51 protruding into the switchover chamber 23 are formed by two channel connectors 52, which are symmetrical on both sides of the axial plane 38 and have an oblong cross section in cross section, the central planes of which are approximately parallel to the axial plane 38 and are parallel to one another. The parts of the nozzle channels 50, 51 projecting into the rotor chamber 26 are formed by separate channel sections 53, each of which is connected to one of the channel connections 52 via a passage opening in the transverse wall 30 and which is connected to the reduced-diameter casing of the front housing part 28 with its turbine wheel 25 Connect opposite sides and narrower in cross-section towards the turbine wheel 25 by the fact that their mutually adjacent walls diverge in cross-section in the direction of the turbine wheel 25, while their mutually facing walls lie essentially parallel to one another in the planes of the associated walls of the duct connection 52. The sides of the channel sections 53 which face the rotor shaft 34 are closed up to the rear end face of the turbine wheel 25 and then open to form the nozzle openings of the drive nozzles 48, 49. The front ends of the channel sections 53 facing away from the transverse wall 30 are open prior to assembly of the end cap 29 and are closed when the end cap 29 is fitted with end closures 54 which project in one piece on the inside of the end wall of the end cap 29, so that manufacture is very simple of the housing in plastic is possible.

The switching device 21 or the switching valve 22 has a switching element 55 which is mounted for carrying out a control movement and which can be pivoted about a relatively small angle about an axis perpendicular to the housing axis, preferably in the axial plane 38, between two end positions and in FIG. 4 in its central position is shown. For pivotable mounting, the switching member 55 has an approximately T-shaped rocker 56, the T-head web lies within the switching chamber 23 and the T-foot forms a movable end plate 31, but sealed with an annular seal 58, so that the switching pin 57 penetrates it the free end of the switching pin 57 protrudes rearward over the end collars 45, 46. The switching mandrel 57 is located between these end collars 45, 46. On both sides of the switching mandrel 57, the rocker 56 on the associated side of the T-head web each has a bearing cutting edge 59 protruding against the end wall 31, with which it cuts in the area of the inner end face of the end wall 31 on both sides the seal 58 is supported so that the pivot axis lies in the plane of this inside and perpendicular to the T-head web in the middle of its length.

The rocker 56 is provided for actuating a plate or strip-like valve body 61 lying essentially parallel to it, which is formed by one leg of an angular profile and between the T-head web of the rocker 56 and the free ends of the nozzle channels 50, 51 and the duct connection 52 lies. The valve body 61 is essentially connected to the rocker 56 only by abutting support, to be precise with the interposition of a strip-shaped leaf spring 60 which only rests on the cam-shaped ends of the T-head web which is concavely curved corresponding to the leaf spring 60, and thereby a structural unit with the valve body 61 forms that it is penetrated closely and axially secured in the middle of its length by a pin of this valve body 61. The other leg of the valve body 61, the against is slightly offset inwards over the adjacent longitudinal edge of the valve body, is securely in contact with the rocker 56 on the side of the T-head web facing away from the housing jacket.

The valve body 61 or its slightly raised end surface regions facing away from the rocker 56 are assigned as valve seats 62 the closely opposite end surfaces of the channel connecting pieces 52, which the valve body 61 is opposite in an axial region of the housing 12, which coincides approximately with the inner end surface of the water inlet connection 33 . In each pivoting end position of the rocker 56, one of the two valve seats 62 is closed and the other is opened, the valve body 61 being initially carried along from the central position according to FIG. 4 via the central connection with the leaf spring 60 and then via one of the cams facing it by the associated cam the rocker 56 can be pressed against the valve seat 62. Against linear movements in the direction of the valve seats 62, the valve body 61 is secured by a counter-holder 63 located between the valve seats 62, which is formed by a web, which, like the duct connection 52, projects freely from the transverse wall 30 and is opposite a central projection of the valve body 61. The valve body 61 is secured against longitudinal displacements by at least one securing means 64 with respect to the housing 12, which is expediently formed by an axial web on the inside of the housing shell and / or on the outer circumference of the connecting piece forming the water inlet connection 33 and in a corresponding groove in the middle of the associated one Longitudinal edge of the valve body 61 engages with sufficient lateral play. The webs forming the fuse 64 also engage in corresponding grooves in the T-head web of the rocker 56 with an even greater lateral play. Once the valve body 61, which is made of rubber-elastic material, is pivoted into a working position, it is closed the water pressure is held in this position until it is transferred back to the other valve position via the rocker 56.

On the hollow shaft 10, an inner ring 46, which is formed by an outer circumferential toothed ring 65 and which meshes with the smaller-diameter output pinion 44 and is axially displaceable relative to it, is rotatably mounted. The running ring 65 is secured against the carrier 5 in a rotationally fixed or form-fitting manner up to a predetermined torque, as a result of which the drive connection between the water motor 11 or the nozzle housing 7 and the stand 3 is established.

The switch device 21 has two ring-like adjusting parts 66, 67, which adjoin the rear end of the housing 12 and adjoin the rear end of the housing 12, one of which adjusts the rear end of the housing 12 or the front collar 45 to adjust the swivel angle and the swivel range surrounds a collar, while the other, identically designed adjusting part 66 projects with its collar in the opposite direction to the rear. The adjusting parts 66, 67 are mounted with two directly adjoining hubs 68, 69 on a bearing sleeve 70 of the carrier 5 projecting freely in the direction of the water motor 11, which surrounds the hollow shaft 10 at a distance and in the region of the hubs 68, 69 a relatively easily overcome Has locking corrugation for the engagement of corrugated segments of the hubs 68, 69 so that the adjusting parts 66, 67 can only be rotated with a predetermined stiffness and hold securely in the respectively set position.

Each adjustment part 66, 67 has a tab-like grip 71, 72 projecting over the outer circumference of its collar, which is located at the end of an outer collar segment of the associated adjustment part 66, 67 in such a way that this collar blows elements as well as the handle lugs 71, 72 are provided in adjoining adjustment parts 66, 67 in a common plane and the collar segment of one handle part in each case overlaps the collar of the other handle part on the outer circumference.

In the adjacent, the collar and the hubs 68, 69 connecting, annular disc-shaped areas of the adjusting parts 66, 67 segment-shaped slots 73, 74 are provided for the engagement or penetration of the switching pin 57, the ends of which form driving stops for the switching pin 57, the Driving stops by mutual rotation of the adjusting parts 66, 67 in their mutual distance and by rotating the adjusting parts 66, 67 in their position relative to an axial or reference plane can be changed.

So that the last-mentioned setting option is limited to a predetermined setting range, a stop 75 of the carrier 5, which protrudes adjacent to the outside of the bearing sleeve 70 and in the same direction as this, is provided, which stops in corresponding slots of the annular disk-shaped areas which are approximately diametrically opposite the slots 73, 74 the adjusting parts 66, 67 engages. So that the rocker 56 or the switching pin 57 cannot be overloaded after reaching its respective end position, a protective pin 76 is provided freely projecting rearward on the housing 12, which is assigned stop surfaces in the ring-shaped areas of the adjusting parts 66, 67, which are opposite the driving surfaces of the slots 73, 74 are correspondingly offset in the circumferential direction and can be formed by stepped end faces of these slots 73, 74. The protective mandrel 76 is located on the side of the switching mandrel 57 facing away from the housing axis 13 and stands freely between the end collars 45, 46 from the end wall 31 to the rear about as far as the switching pin 57 before, so that it also forms a protective shield for the switching pin 57 before the installation of the water motor 11 in the carrier 5.

The mode of operation of the switching device can also be found in DE-PS 19 12 315, to which reference is made for further details and effects.

The output shaft of the water motor 11 formed by the output pinion 44 is drive-connected to the stator 3 with the interposition of an overload clutch 77 located within the carrier 5, which acts between the running ring 55 and the bearing sleeve 70. For this purpose, the race 65 is provided at the end of a cup-shaped intermediate sleeve 88 which is mounted with a predetermined radial clearance within the bearing sleeve 70 and on the hollow shaft 10 in that its rear end forming the bowl bottom is guided directly on the circumference of the hollow shaft 10 while its front end, which has the running ring 65, is mounted on the hollow shaft 10 with the interposition of a guide sleeve 83 inserted into it. The rear end of the intermediate sleeve 78 forms a coupling member 79 of the overload clutch 77, while the other coupling member 80 is formed by an inner, lying between the sleeve ends, penetrated by the hollow shaft 10 ring collar of the bearing sleeve 70, the end facing away from the race 65 for the support an end or shaft collar 84 of the hollow shaft 10 with the interposition of at least one seal 85 or an axial sliding ring.

The rear end face of the coupling member 79 and the front end face of the coupling member 80 have continuous, complementary end teeth 81 over the circumference, the teeth of which have such inclined side flanks on both sides that they become narrower towards their top surfaces. Is between the coupling member 79 and the guide sleeve 83 Within the intermediate sleeve 78 and around the hollow shaft 10, a pre-tensioned coupling spring 82 designed as a helical compression spring is provided, which presses the coupling member 79 of the intermediate sleeve 78 axially displaceably arranged on the guide sleeve 83 into engagement with the coupling member 80. If the housing 12 and the carrier 5 are loaded against one another by excessive torque, the teeth of the coupling members 79, 80 jump over one another, the coupling member 79 being axially displaced against the force of the coupling spring 82 under the flank pressure of the teeth and by a correspondingly fine tooth pitch is achieved that the coupling member 79 returns to its rotational engagement with the coupling member 80 in almost every rotational position.

Between the switching chamber 23 and the rotor chamber 26, a bypass water duct 86 is provided which bypasses the nozzle channels 50, 51, by means of which the amount of water used to drive the water motor 11 is limited to an approximately constant level, irrespective of the amount of water supplied through the water inlet connection 33 to get an almost constant engine speed. The excess amount of water in each case flows through passage openings 87 in the transverse wall 30 outside the outer circumference of the turbine wheel 25 directly into the rotor chamber or against the housing shell, the side surfaces of the channel sections 53 facing away from one another and a platform-like elevation of the transverse wall 30 directed into the rotor chamber 26, from where it is guided with the water emerging to drive the turbine wheel 25 through one of the drive nozzles 48, 49 through the water outlet connection 15 to the spray nozzles 8 of the nozzle housing 7.

The passage openings 87, seen parallel to the axial plane 38 according to FIG. 4, lie on both sides laterally outside the channel sections 53 and, seen at right angles to it or at right angles to the axial plane 38 according to FIG. 3, between the channels sections 53 and the rotor shaft 34 or the platform-like elevation supporting it and the associated ends of the transmission axes 39, 40 holding it close to the inner circumference of the rotor chamber 26. Each passage opening 87 has a pressure relief valve 88, the movable flap-like valve formed by a valve spring tongue 89 Although the valve part works independently of the other valve part, it is, however, formed in one piece with it. The valve seat 90 of each pressure relief valve 88 located within the rotor 26 is formed by an increase in the transverse wall 30 which rises flatly to the housing shell and surrounds the associated passage opening 87, on which the respective valve spring tongue 89 rests flat under a predetermined spring tension. To generate this spring tension, the two valve spring tongues 89 are formed by the widened ends of a flat spring strip 91 made of suitable metal, which in the area of a central widening between the valve spring tongues 89 is penetrated by a bolt 92, for example a self-tapping screw, and with it in the axial plane 38 Attachment is tensioned against the transverse wall 30. When a predetermined pressure gradient between the switchover chamber 23 and the rotor chamber 26 is reached, the valve spring tongues 89 lift off the valve seats 90, so that the bypass water guide 86 is opened as a function of pressure.

On the inside of the end wall of the end cap 29, in addition to the end closures 54, curved, plate-shaped guide members 93 are also provided in one piece, which surround the turbine wheel 25 over part of the outer circumference subsequently to the sides of the drive nozzles 48, 49 or the channel sections 53 which face away from one another, whereby the passage openings 87 are essentially outside the outer circumference of these guide members 93. With its end facing away from the associated drive nozzle 48 or 49, each guide element 93 practically closes the inner circumference of the jacket of the rotor chamber 26 due to the eccentric bearing of the turbine wheel 25 almost on, so that this inner circumference forms a continuation of the guide member and there is a very high efficiency, since the water emerging through the respective drive nozzle 48 or 49, the turbine wheel 85 essentially only in the direction of the water outlet connection 15 can leave.

On the inside of the end wall of the end cap 29 there are further provided one-piece protruding alignment lugs 94 which overlap the channel sections 53 on the sides facing away from one another, so that the end cap 29 can only be placed on the housing part 28 in the correct mounting position. Finally, on the inside of the end wall of the end cap 29, a one-piece protruding axial bearing journal 95 is provided, the tapered end of the end face of which lies opposite a hub of the turbine wheel 25 at a short distance and thereby limits the axial play of the drive rotor 24. Essentially all components of the drive device described can consist of plastic or plastic-like materials, whereby only the leaf spring 60, the clutch spring 82, the spring strip 91 and the bolt 92 as well as the rotor shaft 34 and the transmission axes 39, 40 can consist of metal.

As shown in FIG. 1, the water motor 11 is installed in the nozzle housing 7 in such a way that the gear 19 or the gear chamber 20 lies above the water guide or the switching chamber 23, which is provided at the bottom. As a result, the penetration of water into the gear chamber is prevented even better, and a suitable drain opening or the like can be provided for any leakage water that has penetrated.

Claims (10)

1. Drive device (1) for a sprinkling device (2) or the like., Characterized in that it has a water motor (11) which is provided in a housing (12) with at least one drive rotor (24) exposed to a water guide and in particular a Gearbox (19). 2. Drive device according to claim 1, characterized in that the transmission (19) is arranged in a transmission chamber (20) substantially separate from the water guide, that preferably the transmission chamber (20) through a transverse to the rotor and / or at least one Transverse axis (39, 40) lying transverse wall (30) is separated from a rotor chamber (26) and in particular the drive rotor (24) designed as a drive rotor for driving connection with the Ge drives (19) this transverse wall (30) with a rotor shaft (34) passes through in an essentially sealed manner and that preferably the reduction gear (19) has two parallel transmission axes (39, 40) with alternating intermeshing, stepped gear wheels (41, 42 , 43) and in particular the transmission axes (39, 40) are essentially symmetrical on both sides of an axial plane (38) of a housing shell, in which the rotor axis lies and which possibly forms a central plane of a changeover valve (22) or a changeover chamber (23) . 3. Drive device according to claim 1 or 2, characterized in that for the drive rotation of the water motor (11) in both directions of rotation a switching device (21) is provided, of which in particular a changeover valve (22) lying in the water guide substantially adjacent to the transmission (19 ) is located in a switchover chamber (23) of the water guide, which is sealed off from the gearbox chamber (20) and that preferably the switchover device (21) is transverse to the motor or rotor axis and / or to at least one gearbox axis (39, 40) adjacent to the gearbox (19) and in particular the switchover chamber (23) is separated from the gearbox chamber (20) by an intermediate wall (32) lying approximately parallel to at least one of the axes. 4. Drive device according to one of the preceding claims, characterized in that a turbine wheel (25) receiving rotor chamber (26), the gear chamber (20) and possibly a switchover chamber (23) are surrounded by a common housing shell and in particular the rotor axis with respect to one approximately parallel housing axis (13) is laterally offset from the gearbox (19) and that preferably the switching chamber (23) and the gear chamber (20) extend essentially over the same longitudinal section of the housing (12) and in particular the intermediate wall (32) eccentrically to the housing jacket and to an end water inlet connection (33) for the housing (12) or for the switching chamber ( 23) lies. 5. Drive device according to one of the preceding claims, characterized in that the housing (12) consists essentially of two longitudinally placed housing parts (27, 28), of which preferably a rear housing part (27) essentially a gear chamber (20) optionally with partition (32) and a front housing part (28) essentially a rotor chamber (26), a transverse wall (30), front mounts of gear axles (39, 40) and a changeover valve (22) assigned to the changeover chamber (23 ) projecting duct connection (52) of nozzle ducts (51, 50) for the drive rotor (24). 6. Drive device according to one of the preceding claims, characterized in that a front housing part (28) at its front end with a water outlet connection (15) and water guide members (93) for the drive rotor (24) having an end cap (29) and a the rear housing part (27) is closed with an end wall (31) formed in one piece with it and penetrated by an output pinion (44) of the transmission (19), in which the water inlet connection (33) is provided. 7. Drive device, in particular according to one of the preceding claims, characterized in that the water motor (11) on a, in particular for connection to a stand (3) or the like. The irrigation device (2) designed, support (5) rotatably mounted and via the transmission (19) to this carrier (5), preferably with the interposition of a non-positive self-engaging overload clutch (77). 8. Drive device, in particular according to one of the preceding claims, characterized in that the housing (12) of the water motor (11) with a non-rotatably arranged, in particular in the water inlet connection (33) screwed, hollow shaft (10) is mounted and that preferably With respect to the hollow shaft (10), a running ring (65) for the output pinion (44) of the transmission (19) is rotatably mounted and the running ring (65) is drive-connected to the carrier (5) via an overload clutch (77). 9. Drive device according to claim 7 or 8, characterized in that an overload clutch (77) for a drive connection under spring force intermeshing, frontally toothed coupling members (79, 80), one of which preferably by an end facing away from the transmission (19) The intermediate sleeve (78) which forms the running ring (65) and the hollow shaft (10) relative to the carrier (5) is displaceable relative to the hollow shaft (10) in particular against a coupling spring (82) lying about the hollow shaft (10) is arranged. 10. Drive device, in particular according to one of the preceding claims, characterized in that between the water inlet connection (33) and the water outlet connection (15) of the housing (12) with respect to the flow drive the drive rotor (24) essentially immediate, in particular pressure-dependent controlled bypass. Water supply (86) is provided, which in particular in a transverse wall (30) at least one of the nozzle channels (50, 51) has a separate passage opening (87) from a changeover chamber (23) to a rotor chamber (26) that preferably the bypass water guide (86) is controlled with at least one pressure relief valve (88), which is particularly one in the The rotor chamber (26) has a valve spring tongue (89) covering the passage opening (87) and that in particular both ends of a spring strip (91) lying between the nozzle channels (50, 51) and the rotor axis each form a valve spring tongue (89), each of which laterally covers passage opening (87) located outside an adjacent nozzle duct (50 or 51) or outside the circumference of the turbine wheel (25).

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