EP3892383B1 - Rotor nozzle - Google Patents

Description

The present invention relates to a rotor nozzle as used for high-pressure cleaners.

The present invention relates to a rotor nozzle according to the preamble of claim 1.

Nozzles, in particular for high-pressure cleaners, are referred to as rotor nozzles, which are designed to generate a circulating jet from a fluid, so that the circulating jet sweeps over an at least essentially conical surface.

From the DE 10 037 033 A1 a generic rotor nozzle is already known. This has a nozzle housing which has a swirl chamber between an inflow opening and an outlet opening for fluid. A rotor which is inclined relative to a longitudinal axis of the nozzle housing is arranged in the nozzle housing. The fluid passes through the rotor and exits through the exit orifice of the rotor nozzle, with the orientation of the rotor determining the direction in which the jet exits. Due to the movement of the rotor during operation of the rotor nozzle, the alignment of the rotor and thus the jet direction changes continuously, in particular circumferentially.

The rotor is movably supported on a side facing the outlet opening. This can be done by a foot of the rotor supported in a pan. The rotor has an inlet for the fluid, which can be guided in the rotor and discharged through the outlet opening in the direction of the jet.

During operation, the rotor itself preferably describes an at least essentially conical path of movement or is designed for this purpose. For this purpose, the rotor can be mounted with a bearing on a side facing away from the outlet opening on a bearing part that is rotatable about the longitudinal axis. In the prior art mentioned, this is done by mounting the rotor on a disk rotatably mounted about the longitudinal axis, which has a counterweight to compensate for the centrifugal force caused by the rotor during operation by the counterweight, which is formed by a compensating body.

Compared to others, for example from the DE 10 2006 019 078 A1 known constructions in which the rotor rolls on an inner peripheral surface of the vortex chamber, has the from DE 10 037 033 A1 known solution has the advantage that the resulting imbalance and the resulting vibrations can be reduced by the compensation of the centrifugal force by means of the compensating body. However, it has been shown that, particularly in the case of rotor nozzles with a higher output, the remaining vibrations continue to lead to high wear, stress on the user and corresponding noise development.

It is therefore the object of the present invention to specify a rotor nozzle in which fewer vibrations occur during operation and/or which exhibits less wear.

The above object is achieved by a rotor nozzle according to claim 1. Advantageous developments are the subject matter of the dependent claims.

A proposed rotor nozzle has a nozzle housing which has a turbulence chamber between an inflow opening and an outlet opening, a rotor which is inclined to a longitudinal axis of the nozzle housing being arranged in the nozzle housing and which is movably supported on a side facing the outlet opening and on a side facing away from the outlet opening Side is mounted on a rotatable about the longitudinal axis bearing part. The bearing part can be rotated by a fluid that enters the vortex chamber through the inflow opening.

According to a first aspect of the present invention, the bearing part has a counterweight, which is designed to compensate for a centrifugal force caused by the mass of the rotor during operation. According to the invention, the mass of the counterweight exceeds the mass required to compensate for the centrifugal force, so that (when the rotor nozzle is in operation) a radial component of a recoil caused by the fluid exiting through the outlet opening is at least partially compensated in addition to the centrifugal force. The radial component is a force component that is radial to the longitudinal axis.

According to the proposal, a counterweight is provided that overcompensates for the centrifugal force of the tube. It has surprisingly turned out that in the direction of the centrifugal force there is also a radial component that cannot be neglected acts, which results from the recoil of the fluid exiting the rotor or the rotor nozzle. This radial component is also surprisingly responsible for the fact that, despite the compensation of the centrifugal force, not inconsiderable vibrations occur during the operation of rotor nozzles. Due to the additional weight, the proposed rotor nozzle is also suitable for avoiding vibrations due to the radial component, which has not been taken into account up to now. Surprisingly, this results in a significantly improved concentricity of the rotor, lower vibrations and less wear.

The counterweight or its mass is preferably dimensioned and/or arranged such that the counterweight generates a counterforce at a nominal delivery volume flow of the rotor nozzle, which at least essentially compensates for the sum of the centrifugal force caused by the rotor and the radial component generated by the recoil . As a result, the vibrations during operation of the rotor nozzle can be prevented.

It must be taken into account that the proposed design or dimensioning is also not an obvious measure because in a speed range of the rotor or the rotatable bearing part that is lower than a nominal speed at a nominal delivery volume flow of the rotor nozzle, a certain imbalance results. The reason for this is that the centrifugal force generated by the rotation of the rotor depends on the speed of the rotor or the rotatable bearing part, while the recoil force generated by the escape of the fluid and thus also the radial component of the recoil force, which points in the direction of the centrifugal force, does not depends on the speed, but on the delivery volume flow of the rotor nozzle. Since the counterweight is arranged in the bearing part, the speed of the counterweight always corresponds to the speed of the bearing part or the rotor nozzle, so that the centrifugal force is compensated at any speed with a correspondingly dimensioned and/or arranged counterweight. The additional radial component generated by the recoil, which is also or should be compensated for in the present invention, increases with increasing delivery volume flow and correspondingly increasing recoil.

According to the present invention, the counterweight or its mass is preferably dimensioned and/or arranged in such a way that the counterweight generates a counterforce at a nominal delivery volume flow of the rotor nozzle The sum of the centrifugal force caused by the rotor and the radial component of the recoil is at least essentially compensated. In this way, in normal operation, namely at nominal output volume flow or nominal speed of the rotor or bearing part, the vibrations caused are significantly lower than in the solutions known from the prior art, in which only the centrifugal force caused by the rotor is compensated. Since the nominal output volume flow or the nominal speed is reached very quickly during operation, in particular after a maximum of a few seconds, the imbalance generated by the overcompensation of the forces when "running up" to the nominal speed is not significant, since the advantages the reduced imbalance or the reduced rotations in nominal operation prevail.

The counterweight or its mass is preferably dimensioned and/or arranged such that the sum of the centrifugal force and the radial component is overcompensated when the nominal delivery volume flow is undershot. Alternatively or additionally, the sum of the centrifugal force and the radial component is undercompensated when the nominal delivery volume flow is exceeded.

The arrangement and/or mass of the counterweight is/are preferably changeable and/or the counterweight is exchangeable. This allows the rotor nozzle to be adapted to different desired nominal speeds or nominal delivery volume flows. In particular, the production of the rotor nozzle can be simplified and/or made more economical in this way, since rotor nozzles for different purposes or nominal operations can basically have the same structure and can be easily adapted to a desired nominal speed or a desired nominal delivery volume flow can be done.

The bearing part preferably has one or more weight receptacles, so that the counterweight can be adjusted or varied by inserting different weight bodies into the weight receptacle or weight receptacles. The different weights can differ, for example, in terms of their volume or their size and/or their mass. In particular, different weights can also be provided, which consist of materials of different densities, so that the weights have different masses with the same size or the same volume. This way is one allows easy adjustment of the rotor nozzle to a desired application.

According to one aspect, the counterweight can have or be formed by a plurality of separate weight bodies. In particular, the counterweight can therefore be designed in several parts or consist of or have several and/or separate components or weight bodies.

According to a further aspect of the present invention that can also be implemented independently, the bearing part has a blade part with blades, via which the bearing part can be set in rotation. This achieves a particularly effective and efficient conversion of the kinetic energy of the fluid flowing through the rotor nozzle into rotational energy of the bearing part or rotor. In addition, it has been shown that wear can be reduced in this way and vibrations of the rotor nozzle during operation can be further reduced.

The bearing part is particularly preferably multi-part, with the bearing part--in particular in addition to the blade part--having a bearing device which is coupled to the blade part in a rotationally fixed manner and which has or forms a bearing for the rotor. In particular, the bearing device is thus formed by a component that is separate from the blade part.

Particularly preferably, different bearing devices can be coupled to the blade part, the bearing devices differing in the, in particular, radial, position of the bearing for the rotor and/or in the, in particular, radial, position of the counterweight. As a result, a simple adaptation of the rotor nozzle to different purposes and a cost-effective production of the rotor nozzle are made possible. In particular, the different bearing devices thus make it possible to vary the position of the bearing, the position of the counterweight and/or the relative position of the bearing and the counterweight to one another. Since the centrifugal force acting on a body moving on a circular path depends on the radius of the circular path, the centrifugal force generated by the rotor and/or the centrifugal force generated by the counterweight to compensate for the centrifugal force of the rotor can be adjusted. In addition, a simple adjustment of the jet pattern generated by the rotor nozzle, such as in particular the opening angle of a cone swept by the jet, is made possible.

The inflow opening preferably has an outlet direction which runs transversely to a radial direction or encloses an angle with a radial direction. The angle is preferably greater than 0°. In particular, the angle is an acute angle, an angle of more than 0° and at most 90° being understood as an acute angle. Inflow openings are usually used in the prior art, which run radially to the longitudinal axis of the nozzle housing, so that a fluid exiting from the inflow opening or entering the vortex chamber strikes the nozzle housing perpendicularly. In contrast to this solution, the proposed arrangement or orientation of the inflow opening can reduce wear, improve efficiency during operation of the rotor nozzle and reduce the occurrence of unwanted vibrations. This is achieved in particular by changing, in particular reducing, the angle at which the fluid entering the vortex chamber meets the nozzle housing through the proposed arrangement or orientation of the inflow opening, so that a lower force or a lower fluid pressure occurs the nozzle housing works.

The bearing preferably has a pressure-loaded bearing element, by means of which the rotor is mounted at least essentially without play. In particular, this reduces wear.

According to a further aspect, the counterweight can be movable or displaceable, so that a distance between the center of gravity of the counterweight and the longitudinal axis can be changed as a function of a rotational speed of the bearing part and/or as a function of a discharge volume flow. In particular, the counterweight can be moved or shifted in such a way that the distance of the counterweight or its center of gravity from the longitudinal axis increases with increasing rotational speed of the bearing part and/or with increasing discharge volume flow. This increases in particular the centrifugal force generated by the counterweight. This preferably results in an automatic adjustment of the compensation by the counterweight, so that the rotor nozzle has improved vibration properties and/or wear properties in an increased speed range or delivery volume flow range.

Fig. 1

eine schematische Darstellung eines Hochdruckreinigers mit einer vorschlagsgemäßen Rotordüse;

Fig. 2

eine schematische perspektivische Darstellung einer vorschlagsgemäßen Rotordüse;

Fig. 3

einen schematischen Teilschnitt der vorschlagsgemäßen Rotordüse;

Fig. 4

einen Querschnitt der vorschlagsgemäßen Rotordüse; und

Fig. 5

einen vergrößerten Ausschnitt aus Fig. 4.

Further advantages, features, properties and aspects of the present invention result from the claims and the following description of a preferred embodiment based on the drawing. It shows:

1

a schematic representation of a high-pressure cleaner with a proposed rotary nozzle;

2

a schematic perspective view of a proposed rotor nozzle;

3

a schematic partial section of the proposed rotor nozzle;

4

a cross section of the proposed rotor nozzle; and

figure 5

an enlarged section 4 .

In the figures, the same reference numbers are used for the same or similar parts, with corresponding or comparable advantages and properties being able to be achieved even if a repeated description of these is dispensed with.

1 shows a proposed rotor nozzle 1 for a high-pressure cleaner 2.

In the example shown, the rotor nozzle 1 forms part of the high-pressure cleaner 2 or is fluidly connected thereto, so that a fluid F that is pressurized and made available by the high-pressure cleaner 2 can be or is delivered via the rotor nozzle 1 . In particular, the rotor nozzle 1 forms the tip of a lance 3 for the high-pressure cleaner 2. The rotor nozzle 1 can be supplied with the fluid F via the lance 3. In addition, it can be provided that the lance 3 has a valve and/or is connected to the high-pressure cleaner 2 with a hose 4, so that fluid F provided by the high-pressure cleaner 2 can be discharged via the hose 4 and the lance 3 and ultimately via the rotor nozzle 1 .

Instead of the lance 3, a pistol or the like can also be provided.

The high-pressure cleaner 2 is preferably a manually operated high-pressure cleaner 2 and is preferably used in the private sector, for example for cleaning the outside of buildings such as houses, garages or parts thereof, for example outside walls, roofs, terraces and so on. Another preferred area of use for the high-pressure cleaner 2 is the cleaning of vehicles, particularly in the private sector. In principle, however, other areas of use for the high-pressure cleaner 2 are also possible.

The proposed rotor nozzle 1 is therefore designed in particular for use with a high-pressure cleaner 2 . In principle, however, the rotor nozzle 1 can also be used in other areas.

2 shows a schematic perspective view of a proposed rotor nozzle 1.

The rotor nozzle 1 has a nozzle housing 5

The rotor nozzle 1 or the nozzle housing 5 has a longitudinal axis L.

The longitudinal axis L preferably represents a central axis, main axis and/or main extension axis of the rotor nozzle 1 or the nozzle housing 5. Directional information such as "axial", "radial" or the like preferably refers to the longitudinal axis L below.

The nozzle housing 5 and/or the rotor nozzle 1 is preferably at least substantially symmetrical, in particular rotationally symmetrical and/or cylindrically symmetrical, to the longitudinal axis L.

The rotor nozzle 1 or the nozzle housing 5 has, in particular at one axial end, an outlet opening 6 through which fluid can emerge from the rotor nozzle 1 or can be discharged from the rotor nozzle 1 . The fluid F exits the rotor nozzle 1 in particular as a fluid jet.

On the side facing away from the outlet opening 6, the rotor nozzle 1 or the nozzle housing 5 is preferably for connection to a dispensing device for the Fluid F, in particular the lance 3 formed. For this purpose, for example, a mounting means such as a thread and/or a sealing means such as one or more O-rings can be provided.

In 3 1 shows the inner workings of the rotor nozzle 1 in a schematic perspective view in which the nozzle housing is shown as a section.

4 shows a sectional view of the rotor nozzle 1. In particular, in 1 the inner workings of the rotor nozzle 1 are also shown in section, so that further details and in particular a path W, which the fluid F takes through the rotor nozzle 1, can be seen. The path W is referred to as the fluid path W below.

The rotor nozzle 1 has an inflow opening 7 for the fluid F. The inflow opening 7 preferably has a plurality of separate openings 7A or is formed as a result. In particular, the inflow opening 7 or the openings 7A are formed by a plurality of bores.

The rotor nozzle 1 or the nozzle housing 5 has a vortex chamber 8 . The vortex chamber 8 is preferably formed and/or delimited at least in sections by the nozzle housing 5 . The vortex chamber 8 is arranged or formed between the inflow opening 7 and the outlet opening 6 . The fluid F can enter the vortex chamber 8 through the inflow opening 7 . The fluid F can leave the rotor nozzle 1 via the outlet opening 6, in particular in the form of a fluid jet.

The pressure of the fluid F in the vortex chamber 8 when the rotor nozzle is in operation is usually several hundred bars, for example at least 200 bars or more and/or at most 500 bars or less.

The rotor nozzle 1 has a rotor 9 . The rotor 9 is arranged in the nozzle housing 5 or in the vortex chamber 8 . The rotor 9 can be moved in the vortex chamber 8 , in particular it can be rotated about the longitudinal axis L . Furthermore, the rotor 9 is inclined to the longitudinal axis L. The longitudinal axis L preferably corresponds to an axis of symmetry of the cone or truncated cone over which the rotor 9 or the fluid F sweeps with its jet direction S.

The rotor 9 preferably has the outlet opening 6 or the rotor 9 opens into the outlet opening 6.

In any case, the rotor 9 is fluidically connected to the outlet opening 6 in such a way that during operation the fluid F flows through the rotor 9 and from the rotor 9 to the outlet opening 6 and exits from the rotor nozzle 1 there.

The rotor 9 is movably supported on the side facing the outlet opening 6 . The rotor 9 can be mounted in a bearing pan 10, in particular on the outlet opening side. In this case, the bearing socket 10 is part of the nozzle housing 5 or is connected to the nozzle housing 5 . Furthermore, the rotor 9 preferably has a rotor tip 11 which corresponds to or has a complementary shape to the bearing pan 10 , so that a preferably at least essentially fluid-tight seat of the rotor tip 11 in the bearing pan 10 is made possible.

The rotor 9 is preferably rotatably mounted in the bearing pan 10 . Here it is provided in particular that the rotor 9 performs a wobbling movement, in particular on an at least essentially conical path which is symmetrical to the longitudinal axis L. Accordingly, the movement or movability of the rotor 9 results in a jet direction S of the fluid F, which during operation also sweeps over an at least essentially conical basic shape, with the angle enclosed between the jet direction S and the longitudinal axis L preferably being at least essentially constant and / or an angle between the longitudinal axis L and a center or symmetry axis of the rotor 9 corresponds. The center or symmetry axis of the rotor 9 corresponds to the jet direction S in the example shown.

The rotor nozzle 1 has a bearing part 12 which is mounted so as to be rotatable about the longitudinal axis 9 . The bearing part 12 preferably has a bearing 13 for mounting the rotor 9 , in particular a rotor end 14 of the rotor 9 facing away from or opposite the rotor tip 11 . The rotor 9 or the rotor end 14 is mounted on the bearing part 12 or bearing 13 .

The rotor 9 is therefore preferably mounted with its rotor tip 11 in the bearing socket 10 at one end, which forms the outlet opening 6 or opens into it, and is mounted on the bearing 13 of the bearing part 12 on another, preferably opposite side, so that the rotor 9 a rotary movement of the bearing part 13 following is guided along the previously explained movement with its center or axis of symmetry, which in this case corresponds to the beam direction S.

The rotor 9 is preferably designed and/or arranged or mounted in such a way that it does not come into contact with the nozzle housing 5 . In particular, the rotor 9 does not roll off the nozzle housing 5 during its rotational or tumbling movement, as is the case with some solutions known from the prior art.

The fluid path W through the rotor nozzle 1 is indicated with dashed lines. The fluid path W initially extends from the inflow opening 7 into the vortex chamber 8. The inflow opening 7 is designed and arranged such that the fluid F rotates in the vortex chamber 8 and in particular around the longitudinal axis L (not shown).

The rotation of the fluid F in the vortex chamber 8 brings about the rotational movement or wobbling movement of the rotor 9 .

Starting from the vortex chamber 8 , the rotor nozzle 1 is constructed in such a way that the fluid F is guided through the rotor 9 to the outlet opening 6 . In this case, the outlet opening 6 is preferably formed by the rotor 9 .

The rotor 9, also referred to as a stilt or nozzle body, is preferably designed so that the fluid F flows through it, as a result of which the fluid F reaches the outlet opening 6 from the turbulence chamber 8 and can be discharged through the outlet opening 6.

The bearing part 12 has a counterweight 15 which is designed in any case to compensate for a centrifugal force 16 which is caused or can be caused by the mass of the rotor 9 during operation.

In addition to compensating for the centrifugal force 16 caused by the mass of the rotor 9 during operation, the counterweight 15 is designed to compensate for a radial component 18 of a recoil 17 that occurs during operation of the rotor nozzle 1 as a result of the fluid F escaping from the outlet opening 6.

The recoil 17, that is to say the force which arises as a result of the ejection of the fluid F, is antiparallel to the jet direction S and is therefore inclined to the longitudinal axis L due to the inclination of the jet direction S with respect to the longitudinal axis L.

In relation to the longitudinal axis L, the recoil 17 can be broken down into a force component directed parallel to the longitudinal axis L and a force component directed perpendicularly or radially, in particular outwards, to the longitudinal axis L. The force component directed perpendicularly or radially to the longitudinal axis L is abbreviated as the radial component 18 .

this is in 3 indicated and in particular in figure 5 shown showing an enlarged detail of 4 indicates.

The force component directed parallel to the longitudinal axis L does not change at a constant delivery volume flow and is unproblematic when the rotary nozzle or a high-pressure cleaner 2 is in operation.

The radial component 18, on the other hand, changes its direction continuously as a result of the rotational or tumbling movement of the rotor 9 and the continuous change in the jet direction S that is produced as a result. In particular, the direction of the radial component 18 corresponds at least essentially to the direction of the centrifugal force 16.

In the present invention, it was recognized that with the pressures of the fluid F normally used when operating a high-pressure cleaner 2 or the rotor nozzle 1, the recoil 17 and in particular the radial component 18 are not negligible, but rather, in addition to the centrifugal force 16, to a Imbalance and the resulting vibrations. It has been shown that the radial component 18 can be several Newtons, for example 10, 20 or 30 N.

To compensate for the radial component 18 in addition to compensating for the centrifugal force 16, the mass of the counterweight 15 exceeds that for compensating for the centrifugal force 16 caused by the rotor 9. In this way, the radial component 18 in particular can be compensated.

In other words, the counterweight 15 has an additional mass, the additional mass representing that portion of the mass of the counterweight 15 by which the mass of the counterweight 15 exceeds the mass required to compensate for the centrifugal force 16 .

The radial component 18 is preferably at least essentially compensated for by the counterweight 15 or its additional mass, which advantageously leads to low-vibration operation of the proposed rotor nozzle 1 .

The rotor nozzle 1 is preferably designed or adapted for operation with a specific fluid pressure (nominal pressure) and/or a specific speed of the rotor 9 (nominal speed) and/or for delivering a defined delivery volume flow through the outlet opening 6 . This fixed delivery volume flow is referred to in particular as the nominal delivery volume flow.

The nominal speed of the rotor 9 is preferably more than 2000 and/or less than 10,000 revolutions per minute, for example about 5000 or 6000 revolutions per minute.

The centrifugal force 16 (to be compensated) is understood here in particular as the centrifugal force 16 or the amount of the centrifugal force 16 that is generated by the rotation of the rotor 9 in nominal operation, i.e. at a predetermined speed (nominal speed) and/or a predetermined output current (nominal -Discharge volume flow), for which the rotor nozzle 1 is provided, arises.

The nominal speed is preferably a speed of the rotor 9 at a specified operating point, a specified fluid pressure of the fluid F, a specified exit speed of the fluid F from the outlet opening 6 or at a specified delivery volume flow of fluid F per unit of time, which flows out of the outlet opening 6 is delivered.

The amount of recoil 19 depends on the operating point of rotor nozzle 1 . In particular, the amount of recoil 19 depends on the operating pressure of the fluid F, on the delivery volume flow of the fluid F and/or the exit speed of the fluid F from the exit opening 6 . In this case, the delivery volume flow is the volume of fluid F per unit of time that is delivered from the outlet opening 6 and the delivery speed is the speed of the fluid F as it emerges from the outlet opening 6.

The counterweight 15 or its mass is preferably dimensioned or selected and/or arranged in such a way that the counterweight 15 generates a counterforce 19 at a nominal output volume flow of the rotor nozzle 1, which at least essentially corresponds to the sum of the centrifugal force 16 and the radial component 18 compensated. In other words, the counterweight 15 or its mass is preferably selected and/or arranged such that the counterforce 19 is antiparallel to the centrifugal force 16 and/or the radial component 18 and/or the amount of the sum of the centrifugal force 16 (in nominal Operation) and the radial component 18 corresponds.

The counterforce 19 is in particular the centrifugal force generated by the rotation of the counterweight 15 or the centrifugal force that acts on the counterweight 15 during rotation.

Furthermore, the counterweight 15 or its mass is preferably dimensioned and/or arranged in such a way that the sum of centrifugal force 16 and radial component 18 is overcompensated if the nominal delivery volume flow is not reached and/or if the nominal delivery volume flow is exceeded, the sum of centrifugal force 16 and Radial component 18 is undercompensated.

Weight compensation is preferably provided which, after 100 percent compensation for the vibration-generating (rotor) centrifugal force 16, reduces a design-related second vibration-generating force in rotor nozzles 1, in particular the radial component 18, by at least 5% (preferably 10%, in particular 15%) and/or a maximum of 190% (preferably 180%, in particular 170%) compensated. The second vibration-generating force can preferably be calculated using the performance parameters implemented on the rotor nozzle 1 , in particular the nominal delivery volume flow or volume [l/min], pressure [bar] and/or the angle of inclination of the rotor 9 .

The dimensioning of the counterweight 15 or its mass is preferably such that the radial component 18, in particular at the nominal delivery volume flow, is at least 5%, preferably 10%, in particular 15%, and/or less than 190%, preferably 180%, in particular 170%, is compensated.

The counterweight 15 or its mass is therefore preferably dimensioned and/or arranged in such a way that the radial component 18 (in particular at the nominal speed of the rotor 9 or at the nominal delivery volume flow) is at least 5%, preferably 10%, in particular 15% and/or less than 190%, preferably 180%, in particular 170%, in addition to compensating for only the centrifugal force 16.

The dimensioning of the counterweight 15 or its mass is preferably such that the centrifugal force 16, in particular at the nominal speed of the rotor 9 or the nominal output volume flow, by at least 5%, preferably 10%, in particular 15%, and / or less than 1500%, preferably 1000%, in particular 500%, is overcompensated. The counterweight 15 or its mass is therefore preferably at least 5%, preferably 10%, in particular 15%, and/or less than 1500%, preferably 1000%, in particular 500% heavier than it would be to compensate for the centrifugal force 16 alone .

The counterweight 15 is preferably arranged or can be arranged at least essentially radially opposite the bearing 13 on the bearing part 12 .

The counterforce 19 generated by the counterweight 15 depends on the mass of the counterweight 15 and the position of the counterweight 15 with respect to the longitudinal axis L. FIG. Correspondingly, by changing the position of the counterweight 15 or the position of the center of gravity of the counterweight 15, the counterforce 19 generated can be changed and in particular adapted to different nominal speeds and/or nominal delivery volume flows.

The rotor nozzle 1 is therefore preferably designed in such a way that the arrangement and/or mass of the counterweight 15 can be changed and/or the counterweight 15 can be exchanged.

The counterweight 15 is formed in particular by a separate component that can be inserted into the bearing part 12 and/or removed from the bearing part 12, preferably without an additional tool. This separate component, which forms the counterweight 15, is referred to below in particular as a weight body. The counterweight 15 or the weight body is therefore preferably exchangeable.

The bearing part 12 preferably has one or more weight receptacles 20 . The weight receptacles 20 are each designed to hold the counterweight 15 or a weight body of the counterweight 15 . By providing a plurality of weight receptacles 20, the counterweight 15 can be adjusted in particular, particularly preferably by inserting different weight bodies into the weight receptacle 20 or weight receptacles 20.

The weight receptacles 20 can be arranged on the bearing part 12 at different radial distances from the longitudinal axis L, for example.

As an alternative or in addition, one or more weight receptacles 20 can be provided, which are not arranged radially opposite the bearing 13 but are offset in particular in the circumferential direction to a position radially opposite the bearing 13 . A plurality of weight receptacles 20 are preferably arranged symmetrically to the radial on which or on the extension of which the bearing 13 is arranged. As a result, several weights can be arranged symmetrically to the bearing 13 on the bearing part 12 or inserted into the bearing part 12 and/or any phase shift that may occur between the radial component 18 and the centrifugal force 16 can be taken into account and compensated for by the counterweight 15. In particular at high speeds, it has been shown that the radial component 18 and the centrifugal force 16 can be out of phase with one another, so that the centrifugal force 16 and the radial component 18 point in different directions.

The counterweight 15 can have a plurality of separate weight bodies or be formed by them. The weight bodies can be designed identically or differently. Differently designed weights can differ in particular in terms of their mass, their density, their volume and/or their external shape.

The weight receptacles 20 are preferably formed by recesses in the bearing part 12 that extend axially or parallel to the longitudinal axis L.

Provision can be made for the counterweight 15 to be movable or displaceable - in particular during operation of the rotor nozzle 1 and/or automatically - so that the distance between the center of gravity of the counterweight 15 and the longitudinal axis L depends on the rotational speed of the bearing part 12 and /or in Depending on a delivery volume flow is changeable. It can particularly preferably be provided that the distance of the counterweight 15 or the center of gravity of the counterweight 15 from the longitudinal axis L increases with increasing rotational speed of the bearing part 12 and/or with increasing delivery volume flow.

This can be realized in that the counterweight 15 can be moved within the bearing part 12 or the weight receptacle 20 and is held in a rest position or is urged into a rest position in particular by a spring or the like. The spring or other device can then be designed in such a way that the counterforce 19 of the counterweight 15 exceeds the spring force, by which the counterweight 15 is held in its rest position or is driven into its rest position, from a certain rotational speed and/or from a certain discharge volume flow , so that the counterweight 15, caused by the counterforce 19, is driven radially outward against the spring force and thus shifts its center of gravity. The changed position of the counterweight 15 or its center of gravity then causes an increased counterforce 19, which in turn can compensate for the increased centrifugal force 16 and/or the increased recoil 17 or its radial component 18. In this way, undesired vibrations can be avoided even if a nominal rotational speed is exceeded.

According to an aspect that can be implemented independently, the rotor nozzle 1 or the bearing part 12 preferably has a blade part 21 . The blade part 21 is preferably rotatably mounted about the longitudinal axis L.

The blade part 21 has blades 22 . The blade part 21 or bearing part 12 can be rotated via the blades 22 .

The blades 22 are formed in particular by elements arranged radially from the blade part 21 and in the circumferential direction on the blade part 21 .

In particular, the blades 22 or blade part 21 enable or support a rotation of the bearing part 12 and thus of the rotor 9 , which is coupled to the bearing part 12 , by the fluid F rotating in the vortex chamber 8 . In particular, the blades 22 have or form contact surfaces that extend radially and/or at least substantially parallel to the longitudinal axis L. The blades 22 become the contact surface for the rotating fluid in the vortex chamber 8 Fluid F increases and/or the efficiency in the conversion of the kinetic energy of the fluid F into rotational energy or rotation of the bearing part 12 and/or the rotor 9 is improved.

The bearing part 12 is preferably designed in multiple parts or the bearing part 12 has a number of separate components. In particular, the bearing part 12 has a bearing device 23 in addition to the blade part 21 .

The bearing device 23 represents, in particular, a component that is separate from the blade part 21.

The bearing device 23 is preferably coupled or can be coupled in a rotationally fixed manner to the blade part 21 . In particular, the bearing part 12 is formed by the bearing device 23 and the blade part 21 .

The bearing device 23 preferably has the bearing 13 for the rotor 9 or forms this.

The weight receptacle 20 or weight receptacles 20 is/are preferably delimited at least in sections by the bearing device 23 and at least in sections by the blade part 21 . In particular, the weight mount(s) 20 is/are thus formed between the bearing device 23 and the shovel part 21 or together by the bearing device 23 and the shovel part 21 .

Different bearing devices 23 can be provided, which differ in the position of the bearing 13, in particular the distance of the bearing 13 from the longitudinal axis L, and/or the number and/or arrangement of the weight receptacles 20.

Due to the different positions of the bearing 13, different jet patterns, in particular different angles between the jet direction S and the longitudinal axis L, can be realized, in particular with different bearing devices 23.

The angle between the beam direction S and the longitudinal axis L is preferably more than 5° and/or less than 20°, preferably about 10° to 15°.

The bearing 13 preferably has a bearing element 24 which is subjected to pressure. The rotor 9 or the rotor end 14 is preferably mounted at least essentially free of play by the bearing element 24 . This is conducive to low wear and the prevention or reduction of vibrations.

The rotor end 14 is preferably mounted on the bearing element 24 . The bearing element 24 is pressurized or prestressed in particular in the direction of the rotor 9 or the rotor end 14 . In the example shown, this is realized by a spring 24A, which exerts a force on the bearing element 24 and thus presses the bearing element 24 in the direction of the rotor 9 . In principle, however, other solutions are also possible.

The bearing element 24 or the spring 24A preferably exerts a force both in the axial direction towards the outlet opening 6 and in the radial direction inwards towards the longitudinal axis L, so that the rotor 9 can be seated in the bearing 13 or is mounted with the bearing element 24 .

As already mentioned above, the inflow opening 7 preferably has a plurality of openings 7A or is formed by them.

In particular, the rotor nozzle 1 has an insert 25 which has the inflow opening 7 or openings 7A or in which the inflow opening 7 or the openings 7A are formed.

The insert 25 is preferably inserted or inserted into the nozzle housing 5 on a side facing away from the outlet opening 6 . On a side facing away from the outlet opening 6, the insert 25 preferably has a coupling section 25A for coupling or fluidly connecting, in particular fluid-tight with respect to the environment, the rotor nozzle 1 to the high-pressure cleaner 2 or a part thereof, in particular the lance 3.

The insert 25 or coupling section 25A preferably has an inlet 25B through which the fluid F can enter the insert 25 and thus the rotor nozzle 1 . The inlet 25B is preferably formed by a central recess or bore that is coaxial with the longitudinal axis L. FIG.

The insert 25 preferably has different sections and/or is designed in several parts. In particular, the various sections of the insert 25 are formed by separate components.

The insert 25 or coupling section 25A preferably has one or more passages 25E through which the fluid F can reach the inflow opening 7 from the inlet 25B.

The inflow opening 7 or the openings 7A is/are preferably formed by one or more openings in an inflow section 25C of the insert 25 . The inflow portion 25C is preferably a separate component from the coupling portion 25A.

The inflow opening 7 preferably has an outlet direction 7B which runs transversely to a radial direction. The outlet direction 7B is preferably the direction in which the fluid F passes through the inflow opening 7 or leaves the inflow opening 7 and/or enters the vortex chamber 8 . In particular, the outlet direction 7B is perpendicular to the cross section of the inflow opening 7 and/or parallel to a longitudinal or symmetrical axis of the inflow opening 7 or the opening that forms the inflow opening 7 .

The outlet direction 7B is particularly preferably transverse to the radial line, which leads from the longitudinal axis L to the inflow opening 7 or the respective opening 7A. The outlet opening 7B is preferably at least essentially tangential to the longitudinal axis L.

In other words, the outlet direction 7B encloses an angle with the radial line pointing to the inflow opening 7 or opening 7A. The angle is preferably more than 0° and/or at most 90°.

The outlet direction 7B preferably runs at least essentially parallel to a plane E perpendicular to the longitudinal axis L. In principle, however, the outlet direction 7B can also be inclined with respect to this plane E, in particular in the direction of the vortex chamber 8.

Level E is in 3 indicated by dashed lines. The relative position of the plane E along the longitudinal axis L is preferably of no particular importance, since the plane E merely serves to clarify or define different directions.

Different openings 7A of the inflow opening 7 preferably have different outlet directions 7B. The previous explanations regarding the outlet direction 7B preferably also apply in relation to each individual opening 7A.

The openings 7A are preferably offset in the circumferential direction on the inflow section 25C.

The rotor nozzle 1 preferably has a cross-sectional control of the inlet or inlets for fluid F into the vortex chamber 8 . By controlling or changing the (hydraulic or cumulative) cross section, it is possible to change the flow conditions in the vortex chamber 8 . In particular, it is possible to control or change the rotational acceleration, rotational speed and/or rotational energy of the fluid F set in rotation in the vortex chamber 8, which acts directly or indirectly on the rotor 9 and sets it in rotation.

The control is preferably carried out as a function of the pressure present at the inlet 25B of the rotor nozzle 1 or the rotor nozzle 1 is designed for this purpose. The rotor nozzle 1 can thus be designed for the preferably automatic control of the (hydraulic) cross section of the inlet (or the sum of all inlets) for fluid F into the vortex chamber 8 depending on the pressure of the fluid F at the inlet 25B.

The (hydraulic) cross-section is preferably expanded continuously, steadily, monotonically, strictly monotonically and/or at least substantially proportionally, in particular from a certain threshold pressure, depending on the (further) increase in pressure, or the rotor nozzle 1 is designed for this purpose. The control or controllability of the (hydraulic) cross section of the inlet or inlets into the vortex chamber 8 for the fluid F is particularly preferably a control which is at least essentially or partially at least essentially proportional to the pressure of the fluid F at the inlet 25B .

According to an aspect that can be implemented independently, the rotor nozzle 1 preferably has a bypass 26 and a pressure-controlled valve 27 in addition to the inflow opening 7 . The valve 27 is designed to automatically release the bypass 26 depending on the pressure of the fluid F, so that when the valve 27 is open or the bypass 26 is released, the fluid F can flow through the inflow opening 7 and additionally through the bypass 26 into the swirl chamber 8 can flow in.

The bypass 26 can be released partially. The opening of the valve 27 can therefore take place with a different opening cross section, in particular as a function of the pressure, in particular with an opening cross section of the valve 27 that increases with increasing pressure. The control can take place in this way.

The bypass 26 is preferably an opening—provided in addition to the inflow opening 7—through which the fluid F can enter the vortex chamber 8 . The bypass 26 and the inflow opening 7 preferably (together) form the inlet or inlets into the vortex chamber 8.

The inflow opening 7 is preferably continuously fluidly connected to the vortex chamber 8, in particular without controllability of the (hydraulic) cross section. By contrast, the bypass 26 preferably has the controllable (hydraulic) cross section. Correspondingly, the inlet into the vortex chamber 8 has a (hydraulic) cross section that can only be partially controlled.

The inflow opening 7 preferably opens into the vortex chamber 8 upstream of the bearing part 23, the blade part 21 and/or its blades 22 or on a side of the bearing part 23, the blade part 21 and/or its blades 22 facing away from the inlet of the rotor 9A the fluid F entering through the inflow opening 7 into the vortex chamber 8 on the bearing part 23, the blade part 21 and/or the blades 22. Fluid F escaping through the inflow opening 7 can thereby act on the rotor 9 or the bearing part 23, in particular contribute to driving the rotor 9 or the bearing part 23 or influence the movement of the rotor 9 or the bearing part 23 .

The bypass 26 preferably opens out upstream of the bearing part 23, the blade part 21 and/or its blades 22 or on a side of the bearing part 23, the blade part 21 and/or its blades facing away from the inlet of the rotor 9A 22 into the vortex chamber 8. Accordingly, the fluid F entering the vortex chamber 8 through the bypass 26, preferably in addition to the fluid F flowing through the inflow opening 7 into the vortex chamber 8, acts on the bearing part 23, the blade part 21 and/or the blades 22. In this way or in general, the fluid F escaping through the bypass 26 can (also) act on the rotor 9 or the bearing part 23, in particular contributing to the drive of the rotor 9 or the bearing part 23 or the movement of the rotor 9 or the Affect bearing part 23.

The bypass 26 is preferably closed when the valve 27 is closed, so that when the valve 27 is closed, no fluid F can enter the vortex chamber 8 through the bypass 26 or when the valve 27 is closed, the fluid F can only enter the vortex chamber 8 through the inflow opening 7 .

Opening the valve 27 or releasing the bypass 26 preferably increases the hydraulic cross section through which the fluid F can enter the vortex chamber 8, because the hydraulic cross section consists in particular of the hydraulic cross section of the inflow opening 7 and the hydraulic cross section of the bypass 26.

The valve 27 is in particular a ball valve. Preferably, the valve 27 includes or is formed by a ball 27A and a spring 27B cooperating with the ball 27A. The spring 27B is designed to hold the ball in the bypass 26 in such a way that the bypass 26 is closed or no fluid F can pass through the bypass 26 . In other words, the ball 27A or the valve 27 is biased into a closed position by means of the spring 27B.

The spring 27B is preferably designed such that when a certain fluid pressure is exceeded, the fluid pressure exceeds the force with which the spring 27B biases the ball 27A to a closed position, so that the fluid F pushes the ball 27A towards the spring 27B and the bypass 26 is released.

The fluid pressure at which the valve 27 or the ball 27A releases the bypass 26 can be set by the design of the spring 27B, in particular by the selection of the spring constants.

The fluid pressure at which valve 27 opens or releases bypass 26 is preferably a few bars, for example at least 2 or 3 bars or more and/or at most 10 or 8 bars or less.

The fluid pressure that opens the valve 27 or releases the bypass 26 is preferably the pressure difference between the swirl chamber 8 and the inlet 25B, i.e. the pressure difference between the pressure of the fluid F in the swirl chamber 8 and the pressure of the fluid F at the inlet 25B . The fluid pressure preferably corresponds at least essentially to the pressure loss between the inlet 25B and the vortex chamber 8 or the pressure loss across the inflow opening(s) 7. For this purpose, a side of the ball 27B facing away from the inlet 25B or of another valve element or actuating element of the valve 27 be connected to the vortex chamber 8.

Preferably, a bypass portion 25D of the insert 25 includes or forms the bypass 26 . The bypass section 25D is preferably formed by a separate component.

In the example shown, the bypass section 25D is formed by two components lying against one another, with the bypass 26 being formed or arranged in particular between these two components.

The bypass 26 has an outlet direction 26A.

The outlet direction 26A is preferably the direction in which the fluid F passes through the bypass 26 or leaves the bypass 26 and/or enters the vortex chamber 8 .

The outlet direction 26A of the bypass 26 preferably deviates from the outlet direction 7B of the inflow opening 7 . The outlet direction 26A is preferably inclined relative to the plane E running perpendicularly to the longitudinal axis L.

In particular, the outlet direction 26A of the bypass 26 is more inclined to a plane E perpendicular to the longitudinal axis L than the outlet direction 7B of the inflow opening 7 or the outlet direction 26A of the bypass 26 encloses a larger angle with this plane E than the outlet direction 7B of the inflow opening 7. As "enclosed between the plane E and the outlet direction 7B and 26A respectively "Angle" means in particular the smaller of the angles enclosed between the respective outlet direction 7B, 26A and the plane E.

In particular, the outlet direction 7B of the inflow opening 7 runs perpendicular to the longitudinal axis L or parallel to the plane E or in the plane E. Accordingly, the angle enclosed between the plane E and the outlet direction 7B of the inflow opening 7 is preferably 0°. The included angle between the outlet direction 26A of the bypass 26 and the plane E is in 4 indicated schematically.

In other words, the fluid F flowing through the bypass 26 into the vortex chamber 8 enters the vortex chamber 8 in a different direction or at a different angle (in particular in relation to the plane E) than the fluid F flowing through the inflow opening 7. As a result, the flow of the fluid F in the vortex chamber 8 can be influenced or changed.

The bypass 26 serves in particular to prevent an increase in the speed of the rotor 9 or bearing part 12 above a limit value that is in particular predetermined or specifiable, or to limit the speed of the rotor 9 or bearing part 12 .

An increase in the speed above the limit value can occur in particular if the volume flow of the fluid F through the inflow opening 7 and/or the fluid pressure becomes too high. By releasing the bypass 26 when the fluid pressure is too high, the increase in the speed can be prevented or curbed.

To explain the flow conditions in the vortex chamber 8, it is particularly helpful to view them in adapted coordinates. The movement or speed of each (imagined or real) particle of the fluid F can be divided into a Z component, referred to below as an axial component, a radial component 18 and a tangential component. Here, the axial component is parallel to the longitudinal axis L, the radial component 18 is radial to the longitudinal axis L and the tangential component is perpendicular to the axial component and the radial component 18, so that the components form a three-dimensional Cartesian coordinate system.

The rotation of the bearing part 12 or rotor 9 is in particular decisively influenced or determined by the respective local tangential component of the fluid F or particle. If the bypass 26 now has a different outlet direction than the inflow opening 7, the ratio between the axial component, the radial component 18 and the tangential component of the fluid F or the particles in the vortex chamber 8 is changed, so that an appropriate selection of the outlet direction prevents this in particular it can happen that the tangential component takes on too large a value. This can in turn prevent the - decisively determined by the tangential component - speed of the bearing part 12 is too high or a limit value of the speed is exceeded.

The rotor nozzle 1 or the insert 25 preferably has a plurality of bypasses 26 arranged offset in the circumferential direction on the insert 25 or the bypass section 25D. The previous explanations regarding the bypass 26 and/or the outlet direction 26A preferably apply to each individual bypass 26.

In particular, it can be provided that the multiple bypasses 26 each have a (separate) pressure-controlled valve 27, with the valves 27 having at least two or more different threshold values for the pressure at which the respective bypass 26 is released by the respective valve 27. This enables more precise control or limitation of the speed of the rotor 9 and/or control or limitation of the speed of the rotor 9 over a larger speed range.

In a preferred example, ten bypasses 26 are provided, each having a pressure-controlled valve 27, five of the valves 27 being designed to open at a pressure of, for example, 3 bar or to release the respective bypass 26 and five of the valves 27 being designed to do so are to open the respective bypass 26 at a higher pressure of, for example, 10 bar.

The rotor 9 preferably has an inlet 9A for the fluid F to enter the rotor 9, an outlet 9B for the fluid F to exit the rotor 9, and a channel 28 for guiding the fluid F into the rotor 9 and from the inlet 9A, respectively the outlet 9B. The inlet 9A and the outlet 9B are fluidically connected to one another by the channel 28 .

The inlet 9A preferably forms an opening of the channel 28 to the vortex chamber 8, through which the fluid F can enter the rotor 9 or channel 28 from the vortex chamber 8. The outlet 9B preferably forms the outlet opening 6 and/or opens into the outlet opening 6.

In a preferred, independently realizable aspect, channel 28 has a first, preferably straight, portion 28A and a second, preferably straight, portion 28B. Particularly preferably, the direction of flow of the fluid F in the first section 28A is at least essentially opposite to the direction of flow of the fluid F in the second section 28B. The directions of flow of the fluid F in the channel 28 are in figure 5 indicated by arrows.

In the first section 28A, the flow direction of the fluid F preferably points in a direction away from the outlet opening 6 or the rotor tip 11 and/or in a direction towards the rotor end 14 .

In the second section 28B, the flow direction of the fluid F preferably points in a direction facing away from the rotor end 14 and/or in a direction facing the rotor tip 11 or the outlet opening 6 .

In particular, the channel 28 is tortuous or has a turn or turn.

Preferably, the first section 28A has the inlet 9A and/or the second section 28B has the outlet 9B.

The first section 28A and the second section 28B preferably run at least substantially parallel to a longitudinal axis of the rotor 9.

The inlet 9A is preferably arranged on a side of the first section 28A facing the outlet opening 6 or the rotor tip 11 .

In particular, at least the first section 28A serves as a "calming section" so that the flow of the fluid F is changed from a turbulent flow in the vortex chamber 8 into a laminar flow in the channel 28 or first section 28A. An at least essentially laminar flow preferably prevails in the second section 28B or at least at the outlet opening 6 .

The first section 28A is preferably arranged further outside on the rotor 9 or at a greater distance from a longitudinal axis of the rotor 9 than the second section 28B. In particular, the first section 28A surrounds the second section 28B. The longitudinal axis of the rotor 9 can be congruent with the jet direction S.

The first section 28A is particularly preferably formed by a coaxial tube and/or the second section 28B is formed by a central tube. The central tube and/or the coaxial tube is/are preferably arranged coaxially to the longitudinal axis of the rotor 9 .

The coaxial tube is particularly preferably arranged in a bell shape around the central tube.

The central tube or the second section 28B preferably opens at a first end 29 into the outlet opening 6 and at a second end 30 into the coaxial tube or the first section 28A.

The coaxial tube or second section 28B preferably extends from the inlet 9A to the second end 30 of the second section 28B or central tube.

The rotor 9 is thus preferably designed in such a way that the fluid F first enters the rotor 9 or the channel 28 on an outside through the inlet 9B. In the first section 28A or the coaxial tube, the fluid F then first flows in the direction of the rotor end 14 or in a direction away from or opposite to the rotor tip 11 and/or the outlet opening 6 . The fluid F then passes from the first section 28A into the second section 28B, with the direction of flow of the fluid F being at least essentially reversed. In the second section 28B or the central tube, the fluid F then flows in the direction of the outlet opening 6 or the rotor tip 11.

The rotor nozzle 1 or the rotor 9 preferably has a nozzle 31 . In particular, the nozzle 31 represents a constriction of the channel 28. Preferably, the nozzle 31 represents a portion of the second section 28B or the nozzle 31 adjoins the second section 28B.

The rotor 9 preferably has a nozzle insert 32 which has or forms the nozzle 31 . The nozzle insert 32 is preferably a separate component. In particular, the nozzle insert 32 is inserted into the central tube or fluidically connected to the central tube.

The first section 28A and/or the second section 28B preferably have a plurality of flow guides 33 which are separate from one another and run parallel to one another. As a result, the flow properties in the channel 28 can be improved, in particular a linear and/or laminar flow can be generated or ensured in the channel 28 .

The bypass 26 preferably forms a channel or has a channel. It is further preferred here that the bypass 26 has a channel-shaped inlet to the valve 27 and/or a channel-shaped outlet from the valve 27 into the vortex chamber 8 .

The bypass 26 is preferably a branch. The bypass 26 preferably branches off between the inlet and the inflow opening 7A. In other words, the bypass 26 forms a branch of a tract opening into the inflow opening 7 or the openings 7A or of a structure which conducts the fluid F and extends between the inlet 25B and the inflow opening 7 or the openings 7A.

The bypass 26 is therefore in particular a branch that can be controlled by the valve 27 or can be opened and closed as a function of pressure, which directs fluid F entering the inlet 25B through an opening realized separately from the inflow opening 7 into the turbulence chamber 8 .

Reference list:

1

rotary nozzle

2

high pressure cleaner

3

lance

4

Hose

5

nozzle body

6

exit port

7

inflow opening

7A

opening

7B

Outlet direction of 7/7A

8th

vortex chamber

9

rotor

9A

admission from 9

9B

outlet from 9

10

bearing pan

11

rotor tip

12

bearing part

13

warehouse

14

rotor end

15

counterweight

16

centrifugal force

17

recoil

18

radial component

19

counterforce

20

weight intake

21

blade part

22

shovel

23

storage facility

24

bearing element

24A

Feather

25

mission

25A

coupling section

25B

inlet

25C

inflow section

25D

bypass section

25E

passage

26

bypass

26A

outlet direction of 26

27

Valve

27A

Bullet

27B

Feather

28

channel

28A

first section

28B

second part

29

first end

30

second end

31

jet

32

nozzle insert

33

flow guidance

E

level

f

Fluid

L

longitudinal axis

S

beam direction

W

fluid path

Claims (15)

1. Rotor nozzle (1), in particular for high-pressure cleaners (2), with a nozzle housing (5) which has a swirl chamber (8) between an inflow opening (7) and an outlet opening (6), a rotor (9) which is inclined with respect to a longitudinal axis (L) of the nozzle housing (5) being arranged in the nozzle housing (5), which rotor is movably supported on a side facing the outlet opening (6) and is mounted on a side facing away from the outlet opening (6) on a bearing part (12) which is rotatable about the longitudinal axis (L), wherein the bearing part (12) can be set in rotation by fluid (F) entering the swirl chamber (8) through the inflow opening (7),

   wherein the bearing part (12) has a counterweight (15) which is designed to compensate for a centrifugal force (16) caused by the mass of the rotor (9) during operation,

   characterized in that the mass of the counterweight (15) exceeds the mass required to compensate for the centrifugal force (16), so that, during operation, a radial component (18) of a recoil (17) produced by an exit of the fluid (F) through the outlet opening (6) is at least partially compensated for in addition to the centrifugal force (16).
2. Rotor nozzle according to claim 1, characterised in that the counterweight (15) or its mass is dimensioned and/or arranged in such a way that the counterweight (15) generates a counterforce (19) at a nominal delivery volume flow of the rotor nozzle (1) which at least substantially compensates for a sum of the centrifugal force (16) caused by the rotor (9) and the radial component (18).
3. Rotor nozzle according to claim 1 or 2, characterised in that the counterweight (15) or its mass is dimensioned and/or arranged in such a way that the sum of the centrifugal force (16) and the radial component (18) is overcompensated when the nominal delivery volume flow is undershot and/or the sum of the centrifugal force (16) and the radial component (18) is undercompensated when the nominal delivery volume flow is exceeded.
4. Rotor nozzle according to one of the preceding claims, characterised in that the arrangement and/or mass of the counterweight (15) is/are alterable and/or that the counterweight (15) is exchangeable.
5. Rotor nozzle according to one of the preceding claims, characterised in that the bearing part (12) has one or more weight receptacles (20), so that the counterweight (15) can be adjusted by inserting different weight bodies into the weight receptacle(s) (20).
6. Rotor nozzle according to one of the preceding claims, characterised in that the counterweight (15) comprises a plurality of separate weight bodies.
7. Rotor nozzle according to one of the preceding claims, characterised in that the bearing part (12) has a blade part (21) with blades (22) via which the bearing part (12) can be set in rotation.
8. Rotor nozzle according to claim 7, characterised in that the bearing part (12) is multi-part, the bearing part (12) having a bearing device (23) which is coupled in a rotationally fixed manner to the blade part (21) and which has or forms a bearing (13) for the rotor (9).
9. Rotor nozzle according to claim 7 or 8, characterised in that different bearing devices (23) are couplable to the blade part (21), which differ by the, in particular radial, position of the bearing (13) for the rotor (9) and/or of the counterweight (15).
10. Rotor nozzle according to one of the preceding claims, characterised in that the inflow opening (7) has an outlet direction which is transverse to a radial direction.
11. Rotor nozzle according to one of claims 8-10, characterised in that the bearing (13) comprises a pressurised bearing element (24) by which the rotor (9) is mounted at least substantially free of play.
12. Rotor nozzle according to one of the preceding claims, characterised in that the counterweight (15) is movable and/or displaceable so that a distance of the counterweight (15) and/or its centre of gravity from the longitudinal axis (L) is variable in dependence on a rotational speed of the bearing part (12) and/or a delivery volume flow, in particular increases with increasing rotational speed of the bearing part (12) and/or with increasing delivery volume flow.
13. Rotor nozzle according to one of the preceding claims, characterised in that the counterweight (15) or its mass is thus preferably heavier by at least 5 %, preferably 10 %, in particular 15 %, and/or less than 1500 %, preferably 1000 %, in particular 500 %, than it would be to compensate only for the centrifugal force (16).
14. Rotor nozzle according to one of the preceding claims, characterised in that the counterweight (15) or its mass is preferably dimensioned in such a way that the radial component (18) is compensated for at least 5 %, preferably 10 %, in particular 15 %, and/or less than 190 %, preferably 180 %, in particular 170 %.
15. Rotor nozzle according to one of the preceding claims, characterised in that the rotor nozzle (1) is designed so that the fluid (F) exits through the outlet opening (6) of the inclined rotor (9) as a jet in the direction of the orientation of the rotor (9) and, due to the movement of the rotor (9) during operation of the rotor nozzle (1), the orientation of the rotor (9) and thus the jet direction changes continuously in a circulating manner.

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