DE3419964C2 - Spray head of a high pressure cleaning device - Google Patents

Abstract

To with a spray head on the jet pipe of a high-pressure cleaning device with a nozzle body, which is held on a bearing body rotatably mounted on the jet pipe about an axis of rotation and which has a nozzle bore that generates a point jet, which is directed so that the point jet emitted by it does not coincide with the axis of rotation To obtain a vibration-free run and at the same time to achieve a compact structure, it is proposed that the bearing body is designed as a turbine runner arranged in a housing with turbine blades or turbine ducts, that the housing has an inlet connected to the jet pipe and deflection elements which are passed through the Introduce cleaning fluid entering the inlet against the turbine blades or into the turbine ducts, the turbine blades or turbine ducts and the deflecting elements being designed so that the turbine rotor is rotated about its axis of rotation so that the nozzle bore is also on its inlet side is connected to a collecting space into which the cleaning liquid passes after passing through the turbine blades and turbine ducts, and that the nozzle bore is inclined with respect to the axis of rotation.

Description

15th

The invention relates to a spray head of a high-pressure cleaning device with the features specified in the preamble of claim 1.

With high-pressure cleaning devices that generate a point jet at the spray head of the hand-held spray lance, can είπε surface to be cleaned only by doing this be painted over so that the operator guides the nozzle accordingly. You get a good cleaning effect in the impact area, but there is a risk that the surface to be cleaned will not is evenly painted over.

The evenness of the cleaning can be improved by using flat jet nozzles of nozzles that fan out the jet. However, the liquid particles in the flat jet experience the If the air passes through such a large deceleration that even at a short distance from the spray head none sufficient cleaning effect is more achievable.

It is already known to mount the nozzle body in an oscillating manner for the point jet and thereby the point jet in to move a Schwingiingshewegung (DH-GH 80 29 704). This makes it possible to use a point jet to cover a larger area of a surface to be cleaned to be painted over, but such an oscillating mounting of the nozzle is expensive to construct. aside from that If the jet stays at the reversal points for a disproportionately long time with such nozzles, that one uniform cleaning effect over the entire fanned-out jet cannot be achieved. Through the oscillating movement and the associated forces of inertia are transferred to the Jet pipe, which is difficult for the operator in such an oscillating nozzle body can be held. Working with such a nozzle is therefore very tiring.

Furthermore, a spray head has become known in which a bearing body is freely rotatable about a longitudinal axis is stored (DE-GM 79 29 277). This carries at least one outlet nozzle, which is arranged outside the axis of rotation is and transmits a torque to the bearing body through the recoil of the emitted jet. As a result, the nozzle body moves on a circular path around the axis of rotation, which also causes the point jet is deflected circularly. However, this construction requires, and is, a very bulky structure not possible to direct the jet in any direction, as the recoil forces depend on the jet direction. Only if the beam has a sufficiently large component in the circumferential direction can the desired Rotation of the bearing body can be achieved.

Furthermore, a spray head is known in which a rotary movement of the bearing & örpers by one of the Cleaning fluid-driven turbine takes place via a reduction gear (US-PS 44 07 678). A Such a spray head is extremely complex and not suitable at the free end of a hand-held nozzle to be arranged. Also, with such an arrangement, only one is relative slow rotation of the bearing body possible, so that a flawless movement of the jet pipe is possible Covering the entire area is not guaranteed.

Similar problems arise with a spray head as known from US Pat. No. 3,326,468.

In the field of sprinkler systems, spray heads are known in which the bearing body carrying the nozzles are also set in rotation like a turbine by the liquid to be sprayed itself (US-PS 31 07 056, US-PS 18 62 381). In these arrangements, however, it is desirable that the amount of liquid dispensed in the form of a torn veil, so that a larger area is achieved. These non-generic spray heads Fhd are therefore used for cleaning purposes not suitable, because in terms of cleaning would just be desirable to retain the favorable properties of a compact or point beam and Nevertheless, to be able to cover a large area evenly with such a jet.

It is therefore the object of the invention to provide a spray head of the generic type particularly small, compact and to be built robustly so that it can be used comfortably on a hand-held spray lance. aside from that on the one hand, the spray head should have particularly good cleaning properties of a compact point beam, but on the other hand also with rapid movement of the spray lance enable perfect surface cleaning.

In the case of a spray head, this task is performed by the input ·; described type according to the invention by the in characterizing part of claim 1 specified features solved.

The use of a turbine runner, which at the same time carries the nozzle bore, enables a special -rs compact design, since no gear means or the like are necessary. Also has It was surprisingly found that the pressure losses for the liquid are significantly lower than, for example when a rotating bearing body is driven by the recoil of an exiting point beam. Finally, with such an arrangement, very high speeds can be achieved, for example in of the order of 4000 to 7000 revolutions per minute, so that even with a very fast movement of the jet pipe a surface to be cleaned is completely swept over.

It is particularly beneficial. when the nozzle bore is machined directly into the turbine rotor. Through this The result is a particularly compact design, because only deflecting elements need to be in the housing and the bearing body forming a unit of turbine rotor and nozzle body is arranged be. The turbine runner itself then forms the nozzle body.

In a preferred embodiment, the flow path is trained as a collection room.

The turbine can be flown against axially or radially.

It is advantageous if the nozzle bore in the axis of rotation of the turbine runner or ends at a short distance from it.

This results in an essentially exactly ke-

gel jacket-shaped course of the point beam, whereby through the exit in the axis of rotation or with little Distance from this a particularly smooth running of the bearing body can be achieved, which does not go through lateral forces and tilting moments is influenced. It is particularly advantageous if the turbine runner has a the turbine blades or turbine ducts opposite to the axis of rotation concentric pin which dips into an opening in the housing and the nozzle bore exits through its end face. It This results in a small central opening in the housing, in which the pin and the outlet opening of the Nozzle bore is located, while the housing can be closed all around.

The pin is preferably sealed with respect to the housing, for example can be in the outer wall circumferential grooves are incorporated into the pin, so that a labyrinth gap seal is formed.

The turbine rotor can be in the housing by means of a slide bearing or preferably by means of a ball bearing be stored, which contains alternately steel balls and plastic balls. The plastic balls have in such a ball bearing self-lubricating properties, as there are small bumps in the steel balls close and smooth them out. In addition, particles of dirt can be pressed into the plastic balls. so that they no longer interfere with the operation of the ball bearing in this way. Such a ball bearing thus has also self-cleaning effect.

The ball bearing can be designed as an angular contact ball bearing, it is also the use of axial ball bearings possible.

In a preferred embodiment, flow paths are provided in the housing through which the ball bearing can be acted upon on both sides by the cleaning fluid in the housing. This prevents The cleaning fluid flows through the ball bearing and the permanent lubricating grease it contains is removed from the ball bearing.

In a preferred embodiment, the turbine runner has a cylindrical one that is open towards the inlet Cavity into which an insert receiving the turbine ducts is inserted. This forms between itself and the end wall of the cylindrical cavity the collecting space, while the end wall the Receives nozzle bore or carries a nozzle body receiving the nozzle bore. This will make the Manufacture of the turbine rotor is much easier, especially if the insert is made of plastic.

It can be provided that along the circumference of the insert in this opposite to the direction of the axis of rotation in the circumferential direction inclined grooves are incorporated, which together with the inner wall of the cylindrical Form cavity the turbine channels.

In the case of a turbine with an axial flow against it, the turbine ducts can be in the one opposite the nozzle bore Begin the face of the turbine rotor and run diagonally in the circumferential direction up to the collecting space.

It is provided that a deflecting body is arranged in the housing between the inlet and the turbine rotor is, which on its side facing the turbine rotor emerges obliquely from it in the circumferential direction Has inflow channels which are directly opposite the inlet openings of the turbine channels.

In order to shape the cleaning fluid, which swirls after it leaves the turbine ducts or the turbine blades, into a homogeneous point jet, it is advantageous if the nozzle bore narrows in steps from the collecting space to the outlet end. It has also proven to be advantageous if a rectifier is inserted into the nozzle bore.
In a preferred embodiment, a fluid or eddy current brake limiting the speed of the turbine rotor is provided.

In this case, in the case of a liquid brake, the turbine rotor can have blade-shaped braking elements which

ίο immerse in the cleaning liquid in the housing. That Housing can impede the rotation of the cleaning fluid around the axis of rotation of the turbine rotor Wear braking links.

It can be provided that braking elements are arranged on the outer jacket of the turbine rotor, which Opposite brake members on the inner wall of the housing surrounding the turbine runner, which preferably Include axially parallel grooves in the inside of the housing. Through the interaction of the Shovel-shaped braking elements and the axially parallel grooves are generated in this vortex, which the Limit the turning speed, whereby the braking forces increase with the square of the turning speed, so that at low speed there is a very slight braking effect, which increases with increasing speed amplified so that finally stabilization occurs. A particularly favorable speed is, for example between 3000 and 7000 revolutions per minute.

In a further preferred embodiment it is provided that the turbine rotor on its nozzle bore remote side a sealed by means of a gap seal in a cavity in the housing has immersing journal, and that the cavity via a suction line with an injector in the inflow line through which the cleaning liquid flows. It succeeds in the to bring forces acting axially on the turbine runner essentially in equilibrium. The turbine runner is normally surrounded on all sides by the pressurized cleaning liquid except the one pointing outwards through the opening in the housing Area in which the nozzle bore emerges. As a result, an axial force acts on the turbine runner, which seeks to move this in the direction of the nozzle bore. This force can thereby be balanced be that the bearing pin in the cavity with relative to the pressure of the cleaning fluid lowered Pressure with a suitable cross-sectional area is immersed This can preferably be selected so that that the turbine runner at a certain flow speed of the cleaning liquid, so a certain injector effect, is completely in equilibrium.

In a further preferred embodiment it is provided that the spray head has at least one has further nozzle bore, and that the cleaning liquid entering the spray head from the jet pipe either to the further nozzle bore or to its nozzle bore via the turbine rotor is. In this further nozzle bore, a flat jet nozzle is usually used, so that with a Such a spray head generates a point jet or a flat jet moving along a cone jacket can be.

It is particularly advantageous if the switching device has a chamber with one inlet and two outlets as well as a freely movable valve body around

summarizes, through various orientations in the unpressurized State can optionally be positioned in front of one of the two outlets and by the pressure of the cleaning fluid is then printed in a sealing manner against this outlet.

With the spray head described can be advantageous Way move a point beam along a cone envelope; be, with this configuration at the same time a suction is generated, which the sprayed cleaning liquid and particles of liquid ricocheting off the cleaned surface in the direction of the exit Entrains fluid. This has the additional advantage that the operator can also get through the liquid bouncing off the surface to be cleaned is not reached because the suction presses these liquid particles back onto the surface to be cleaned which will eventually drain the liquid.

With this spray head a particularly favorable cleaning effect can be achieved because the one along the The point beam guided by the cone jacket hits the surface as a point beam with almost unchanged energy. If the operator guides the beam over the area, each area is swept twice in succession, a completely uniform movement of the point jet takes place, which does not cause any vibrations of the jet pipe leads.

The following description of preferred embodiments of the invention serves in context with the drawing for a more detailed explanation. It shows

1 shows a longitudinal sectional view through a first prior art Embodiment of a spray head;

F i g. 2 is a sectional view along line 2-2 in FIG. 1;

F i g. 3 is a sectional view taken along line 3-3 in FIG. 1;

F i g. 4 is a sectional view taken along line 4-4 in FIG. 1;

5 shows a longitudinal sectional view through another preferred embodiment of a spray head;

F i g. 6 is a sectional view taken along line 6-6 in FIG. 5;

F i g. 7 is a sectional view taken along line 7-7 in FIG. 5;

F i g. 8 shows a longitudinal sectional view of a further preferred exemplary embodiment of a spray head;

FIG. 9 is a sectional view along line 9-9 in FIG and

FIG. 10 is a sectional view taken along line 10-10 in FIG. 8.

The in the Fi g. 1 to 4 shown spray head is on the end of a jet pipe 1 of a high-pressure cleaning device, not shown in the drawing, is screwed on.

In high-pressure cleaning devices of this type, the jet pipe is usually connected by means of a flexible high-pressure hose connected to the high-pressure cleaning device and forms part of a manual spray gun, with which a liquid cleaning agent, for example water under high pressure, optionally a chemical is mixed in, can be splashed.

The spray head in the FIG. 1 to 4 illustrated embodiment has a two-part, cylindrical Housing 2 with an inlet part 3 screwed onto the jet pipe 1 and with one on this screwed-on outlet part 4. A plastic cap 5 is pushed over the outlet part 4.

The inlet part 3 and the outlet part 4 together form a cylindrical cavity 6, which on its the The side facing the jet pipe 1 is connected to the jet pipe 1 via an opening 7 in the end wall 8 stands. On the opposite side, there is a central opening in the corresponding end wall 9 10, which is extended to the outside like a collar.

In the outlet-side part of the cavity 6 is a

Turbine rotor 11 about a through the cylinder longitudinal axis formed axis of rotation rotatably mounted. For this purpose is in the cavity 6 on the outlet cable end wall

9, a ring 12 with an L-shaped cross-section is applied, which supports the outer ring 14 of an angular contact ball bearing ί3. The inner ring 15 of the angular contact ball bearing surrounds a central extension 16 of the turbine rotor

ίο 11, which runs out in the form of a 'pivot pin': 12, which dips into the collar-shaped extended 'opening 10 in the end wall 9 on the outward side. The dimensions are chosen so that a gap seal is created between the pivot pin 17 and the inner wall of the opening 10; if necessary, circumferential grooves can be made in the outer wall of the pivot pin 17 so that a labyrinth seal is formed (not shown in FIG. 1).
The angular contact ball bearing 13 preferably comprises in ab-

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made of plastic, so that a self-lubricating and self-cleaning ball bearing is created. The self-lubrication is done by the plastic balls that supply material with the unevenness in the stainless steel balls can be filled out. In addition, dirt, for example metal chips, Press into the plastic balls so that they no longer appear disturbing.

The turbine runner 11 surrounds the extension on its 16 opposite end to the inlet part 3 open towards the cylindrical cavity 19, from which a stepped narrowing nozzle bore 20 emerges. This nozzle bore 20 is opposite the The axis of rotation is inclined by a few degrees, for example by 10 °, and occurs in the area of the end face 21 of the pivot pin 17 out of this. The exit occurs either in the area of the axis of rotation itself or to a small extent Distance from this, since the diameter of the pivot pin 17 compared to the diameter of the turbine rotor 11 itself is low. This diameter can, for example, be in the order of magnitude between 4 and

10 mm.

A rectifier known per se can be arranged in the inlet area of the nozzle bore 20, the contributes to the homogenization of the flow in the nozzle bore. This rectifier is not shown in FIG shown.

In the open end of the cavity 19, a circular cylindrical solid plastic insert is used, which in the cavity is held in a rotationally fixed manner, for example by a press fit. The plastic insert 22 closes with the free edge 23 of the turbine runner 11 and has a height that is less than the height of the Cavity 19, so that between the plastic insert 22 and the end wall 24 closing off the cavity of the turbine rotor 11, a collecting space 25 is formed, from which the nozzle bore 20 emerges.

The plastic insert 22 has circumferential grooves running obliquely in the circumferential direction along its circumference

26, which extend over its entire axial length and thus form turbine ducts from the underside

27 of the plastic insert 22 lead into the collecting space 25.

The underside 27 is provided with radially extending, wing or shovel-shaped braking elements 28, which form a ring lying within the inlet openings 29 of the circumferential grooves 26 (FIG. 2).

In the inlet-side part of the cavity 6 is a Deflection body used, which is the inlet-side part

of the cavity 6 closes off with respect to the rest of the cavity and has circumferential grooves 31 inclined in the circumferential direction on its circumference, which together with the inner wall of the cavity 6 form inflow channels 32 ■. The inflow channels 32 and the circumferential grooves 26 in the plastic insert 22 are at the same distance from the axis of rotation, the outlets of the inflow channels 32 are located opposite the inlet openings 29 of the circumferential minutes 26 at a small distance.
The Um- • .ilenkkörper 30 rotatably connected to the inlet part 3 has on its side facing the turbine runner 11 also a ring of shovel-shaped, radially outwardly extending brake members 33, which are opposite the appropriately designed brake elements 28 of the plastic insert 22 at a small distance .

The outside diameter of the turbine rotor 11 is slightly smaller than the inside diameter of it receiving cavity 6 so that a narrow annular gap is formed between these two parts in the area of the extension 16 of the turbine rotor 11 extended to the ball bearing 13. In the ring 12 are initially axially extending from this enlarged annular gap and then incorporated radially extending channels 34 and 35, which open into an annular space 36 which the Extension 16 of the turbine rotor 11 on the opposite side of the ball bearing 13 surrounds. To this The annular gap is on one side of the ball bearing and the annular space on the other of the ball bearing in connection with each other.

During operation, cleaning liquid under high pressure (e.g. 100 bar) enters through the jet pipe 1 the cavity 6. The cleaning fluid is in the deflecting body 30 passed through the inclined inflow channels 32 and comes out of them into the also inclined circumferential grooves 26 of the turbine rotor 11. By the inclined direction of the A torque is transmitted to the turbine rotor as well as the circumferential grooves that this is set in rotation about its axis of rotation. The cleaning liquid emerging from the circumferential grooves 26 is collected in the collecting space 25 and from there through the nozzle bore 20 to the outside submitted. The nozzle bore is designed so that a point jet is created, that is, a jet that overflows its length does not essentially fan out. Due to the inclination of the nozzle bore in relation to the axis of rotation the point beam emerges on the jacket of a cone, the tip of which is defined by the axis of rotation.

The speed of the turbine rotor is determined by the interaction the braking elements 28 and the braking members 33 limited, which together as a fluid brake works. It is advantageous that the braking effect depends on the square of the speed and thus at low speeds is low.

The pressure losses that the cleaning liquid experiences when flowing through this spray head are extraordinary low, d. H. By driving the turbine rotor, only a very small proportion of the kinetic energy of the incoming cleaning fluid is consumed. needs

Pressurized cleaning fluid, which reaches the ball bearing 13 through the annular gap surrounding the turbine rotor 11, cannot rinse out any lubricating grease from this, since the ball bearing has the; examples e * the channels 34 and 35 are also acted upon on the opposite side of the cleaning fluid, so that overall no flow through the ball bearing passing results. The housing is effectively sealed off from the turbine rotor in the area of the pivot pin 17, so that only a very small proportion of the cleaning fluid escapes through this sliding seat seal.

The turbine runner is rotationally symmetrical except for the nozzle bore built up so that there are hardly any imbalances when the spray head is in operation. Through this a largely vibration-free operation can be achieved.

The in the F i g. 5 to 7 illustrated embodiment a spray head is largely constructed in the same way; Corresponding parts therefore wear the same Reference number.

Differences result primarily from the Use of a thrust ball bearing 40 instead of one: s Angular contact ball bearings. This ball bearing comprises an outlet-side ring 41 and an inlet-side ring 42, between which a ball ring 43 is arranged. The rings and the ball ring surround the extension 16 of the turbine rotor 11 concentrically, the outlet-side ring 41 on the ring 12 and the inlet-side Ring 42 is supported on the end wall 24 of the turbine rotor 11.

In addition, the turbine runner 11 and the Deflection body 30 on the mutually facing sides no braking elements and braking members. Against it is A liquid brake is also provided in this exemplary embodiment, but this is achieved by axially parallel ribs 44 on the circumference of the turbine rotor 11 and through axially parallel grooves 45 in the turbine rotor 11 surrounding inner wall of the housing 2 are formed. The ribs 44 are sawtooth-shaped, see above that a steep edge 46 when passing the grooves 45 generates fluid vortices in this fluid that slows it down of the turbine runner (Fig. 7).

In the one shown in FIG. 5 illustrated embodiment, the housing is not covered by a plastic cap, however, it would be entirely possible to provide a corresponding plastic cap here as well.

Otherwise, the similar structure also results in a similar mode of operation.

In the further illustrated in FIGS Embodiment of a spray head is also chosen a similar structure, wear corresponding parts therefore, the same reference numerals are also used in this exemplary embodiment.

A major difference of the embodiment of Figure 8 is that the inlet part 3 of the Housing is part of a double housing 50, which has two separate outlet systems for the cleaning liquid supplied For this purpose, the double housing 50 forms together with the one screwed into this Outlet part 4 has a cavity 6 in which in the manner explained with reference to the preceding examples a turbine rotor 11 is rotatably mounted, which is set in rotation by the inflow of cleaning fluid and the cleaning fluid after flowing through the turbine ducts via a nozzle bore on a cone shell. In the one shown in FIG. 8 shown embodiment is instead of the ball bearings 13 and 40, a plain bearing 51 is used, so that in this embodiment, the ring 12 with the Channels 34 and 35 are omitted

In addition, the turbine runner 11 has a one that passes through the plastic insert 22 and the deflecting body 30 Bearing pin 52 which dips into a bearing opening 53 in the end wall 8 on the inlet side.

but diibci between its face 54 and the floor 55 of the fluid opening 53 leaves a suction chamber 56 free. The bearing pin forms in the bearing opening 53 a gap seal, so that the suction chamber 56 is largely sealed off from the cavity 6.

The inlet opening 7 for the cleaning liquid is in the embodiment of FIG. 8 as an injector 57 which comprises a suction line 58 connected to the suction chamber 56.

This construction allows the cleaning liquid flowing into the cavity 6 via the injector 57 lower the pressure in the suction chamber 56 significantly below the liquid pressure in the cavity 6, so that the axial forces acting on the turbine rotor in the area of the end face 54 are less than they are would be under the influence of the static pressure of the cleaning liquid in the cavity 6. This is how it is possible to compensate for the pressure forces acting on the turbine rotor in the axial direction. During the The turbine runner is surrounded on all sides by the cleaning fluid under high pressure, one is missing such pressurization in the area of the outlet end face 21. By reducing the pressure in the suction chamber 56 this lack of pressurization can be compensated for, so that the door runner is largely in equilibrium. Complete compensation can be achieved for a given flow velocity the cleaning liquid by a suitable speed of the cleaning liquid by a suitable choice of the size of the face can be achieved.

Such a pressure relief by providing a suction chamber and an injector can also be used in the The embodiments described above are used, the same applies to the different storage of the turbine rotor.

The double housing 50 now also takes place in the turbine rotor still has a second liquid channel 59, which runs parallel to the cylindrical cavity 6 ur.d opens into a nozzle body 60 with a nozzle bore 61. The nozzle bore 61 runs parallel to the 'Axis of rotation of the turbine rotor 11 and ends essentially in the same plane as the nozzle bore 20 in the turbine rotor. The nozzle body and nozzle bore are designed so that they generate a fanned out flat jet.

A switching chamber 62 is arranged in the end of the double housing 50 connected to the supply line, which are connected via an inlet 63 to the supply line and via an outlet 64 or 65 to the injector 57 or the channel 59 is in communication. Inside the switching chamber 62 is a spherical valve body 66 freely movable when pressed against one of the two outlets 64 or 65 designed as a valve seat can close this.

If the supply of cleaning liquid is switched off, d. H. the interior of the switching chamber 62 is made pressureless, then the valve body 66 can move freely in the switching chamber 62, so that you can by appropriate Orientation of the spray head can achieve that the valve body either in the area of the one outlet 64 or in the area of the other outlet 65. When switching on the pumping of the cleaning liquid the valve body is then firmly against the corresponding one by the cleaning fluid Pressed outlet and closes it, so that the cleaning liquid flow through the other outlet In this way it is possible in a simple manner, between a flat jet (via the nozzle body 60) or a circumferential one along a conical jacket Switch point jet (through the turbine runner 11).

Here, too, it should be noted that a double housing 50 with a flat jet nozzle and a switchover option, also in combination with the above described spray heads can be used.

The turbine rotors can also have differently designed turbines, for example, instead of the Turbine channels may be provided turbine blades. The flow can also be used instead of in the axial direction . Take place in the radial direction, as is known per se in turbine construction.

Production is facilitated if the turbine rotor is in the rotor housing as an injection-molded part with the grooves on the Scope is designed so that it can be made from a split mold without reworking. It is cheap. even if the bearing body is an injection-molded part that is manufactured in a corresponding manner.

Instead of the discussed fluid brake or an eddy current brake, a centrifugal brake could also be used Find use.

In addition 5 sheets of drawings

Claims (25)

Patent claims: 1. Spray head of a high-pressure cleaning device with a nozzle that is attached to an axis of rotation rotatable bearing body is arranged and generates a point beam whose longitudinal axis is not with the axis of rotation coincides with one of the cleaning fluid flowed through the turbine, which drives the bearing body around the axis of rotation, and with a flow path in the bearing body through which the cleaning fluid after flowing through the Turbine reaches the nozzle bore, thereby characterized in that the bearing body itself is arranged as a turbine rotor in a housing (2; 50) (11) is formed and that the nozzle bore (20) opposite the axis of rotation of the turbine rotor (11) is inclined at an acute angle 2. Spray head according to claim 1, characterized in that dzß the nozzle bore (20) immediately in Hpn Tnrhir ^ nlänfpr / I1 ^ pincrpnrhiMtPt i ^ t v. _x j _σ 3. Injection head according to claim 1 or 2, characterized in that the flow path as a collecting space (25) is formed. 4. Spray head according to one of the preceding claims, characterized in that the turbine rotor (11) is axially flown against. 5. Injection head according to one of claims 1 to 3, characterized in that the turbine rotor (11) is radially flown against. 6. Injection head according to one of the preceding claims, characterized in that the nozzle bore (20) ends in the axis of rotation of the turbine rotor (11) or at a small distance therefrom. 7. Spray head according to one of the preceding claims, characterized in that the turbine rotor (11) one of the turbine blades or turbine ducts (Circumferential grooves 26) has opposite pins (17) which are concentric to the axis of rotation, which dips into an opening (10) in the housing (2; 50) and the nozzle bore through its end face (21) (20) exits. 8. Injection head according to claim 7, characterized in that the pin (17) opposite the housing (2; 50) is sealed. 9. Injection head according to claim 8, characterized in that in the outer wall of the pin (17) Circumferential grooves are incorporated. 10. Injection head according to one of the preceding claims, characterized in that the turbine rotor (11) is mounted in the housing (2; 50) by means of a ball bearing (13; 40) which alternately Contains steel balls and plastic balls. 11. Injection head according to claim 10, characterized in that that in the housing (2) flow paths (Ka-Haie 34. 35) are provided, through which the ball bearing (13; 40) on both sides of the cleaning liquid can be acted upon in the housing (2). 12. Injection head according to one of the preceding claims, characterized in that the turbine rotor (11) has a cylindrical cavity (19) which is open towards the inlet (7) and into which the Turbine channels (circumferential grooves 26) receiving insert (22) is inserted that the insert (22) between itself and the end wall (24) of the cylindrical view Cavity (19) forms the collecting space (25), and that the end wall (24) the nozzle bore (20) picks up or one pick up the nozzle bore carries the nozzle body 13. Spray head according to claim 12, characterized in that j shows that the insert (22) is made of plastic j 14. Injection head according to claim 13, characterized in that along the circumference of the insert (22) machined into these grooves (26) inclined in the circumferential direction with respect to the direction of the axis of rotation are, which oilden the turbine ducts together with the inner wall of the cylindrical cavity (19). 15. Injection head according to one of claims 1 to 4 or 6 to 14, characterized in that the turbine channels in the end face (27) of the turbine rotor opposite the nozzle bore (20) (11) and run diagonally in the circumferential direction to the collecting space (25). 16. Injection head according to claim 15, characterized that in the housing (2; 50) between inlet (7) and turbine rotor (11) a Umlcnkkörper (30) is arranged on its side facing the turbine rotor (11) in the circumferential direction has A.nströmkanäle (32) emerging from it obliquely which are directly opposite the inlet openings (29) of the turbine ducts (circumferential grooves 26). 17. Injection head according to one of the preceding claims, characterized in that the nozzle bore (20) siu.T narrows in steps from the collecting space (25) to its outlet end 18. Spray head according to one of the preceding claims, characterized in that in the nozzle bore (20) a rectifier is used 19. Injection head according to one of the preceding claims, characterized in that a die Fluid, eddy current or centrifugal brake limiting the speed of the turbine rotor (11) is provided 20. Injection head according to claim 19, characterized in that that the turbine runner (11) has blade-shaped braking elements (28; ribs 44), which in Immerse the cleaning liquid in the housing (2; 50). 21. Injection head according to claim 20, characterized in that the housing (2; 50) the rotation of the Brake elements (33; grooves) which impede cleaning fluid around the axis of rotation of the turbine rotor (11) 45) carries 22. Injection head according to claim 21, characterized in that that braking elements (ribs 44) are arranged on the outer jacket of the turbine rotor (11), those braking members (grooves 45) on the inner wall of the housing surrounding the turbine runner (11) (2:50) opposite. 23. Injection head according to one of the preceding claims, characterized in that the turbine rotor (11) on its side facing away from the nozzle bore is sealed by means of a gap seal in a cavity (suction chamber 56) in the housing (50) immersing bearing journals (52) and that the cavity (suction chamber 56) via a suction line (58) with an injector (57) in the inflow line through which the cleaning liquid flows. * '# j 24. Spray head according to one of the preceding claims, characterized in that it is still has at least one further nozzle bore (61) and that from the jet pipe (1) into the Cleaning liquid entering the spray head either from the further nozzle bore (61) or via the turbine rotor (11) whose nozzle bore (20) can be fed 25. Injection head according to claim 24, characterized in that the switching device comprises a chamber (62) with an inlet (63) and two outlets (64,65) and a freely movable valve body (66) which is in the depressurized state by different orientation one of the two outlets (64 or 65) po £ ^; can be lionized and is then pressed sealingly against this outlet (64 or 65) by the pressure of the cleaning liquid.