EP4197643A1 - Buse à géométrie de faisceau réglable, ensemble buse et procédé de fonctionnement d'une buse - Google Patents

Buse à géométrie de faisceau réglable, ensemble buse et procédé de fonctionnement d'une buse Download PDF

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Publication number
EP4197643A1
EP4197643A1 EP22214712.6A EP22214712A EP4197643A1 EP 4197643 A1 EP4197643 A1 EP 4197643A1 EP 22214712 A EP22214712 A EP 22214712A EP 4197643 A1 EP4197643 A1 EP 4197643A1
Authority
EP
European Patent Office
Prior art keywords
fluid
valve
swirl chamber
nozzle
flow
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP22214712.6A
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German (de)
English (en)
Inventor
Lisa PARSCHAT
Dr. Hannes KÖHLER
Sebastian KRICKE
Dr. Enrico FUCHS
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Technische Universitaet Dresden
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Technische Universitaet Dresden
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Filing date
Publication date
Application filed by Technische Universitaet Dresden filed Critical Technische Universitaet Dresden
Publication of EP4197643A1 publication Critical patent/EP4197643A1/fr
Pending legal-status Critical Current

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/12—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means capable of producing different kinds of discharge, e.g. either jet or spray
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/30—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to control volume of flow, e.g. with adjustable passages
    • B05B1/3006—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to control volume of flow, e.g. with adjustable passages the controlling element being actuated by the pressure of the fluid to be sprayed
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/34—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl
    • B05B1/3405—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl
    • B05B1/341—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet
    • B05B1/3421—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with channels emerging substantially tangentially in the swirl chamber
    • B05B1/3426—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with channels emerging substantially tangentially in the swirl chamber the channels emerging in the swirl chamber perpendicularly to the outlet axis
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/34—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl
    • B05B1/3405—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl
    • B05B1/341—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet
    • B05B1/3484—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to influence the nature of flow of the liquid or other fluent material, e.g. to produce swirl to produce swirl before discharging the liquid or other fluent material, e.g. in a swirl chamber upstream the spray outlet with a by-pass conduit extending from the swirl chamber
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B12/00—Arrangements for controlling delivery; Arrangements for controlling the spray area
    • B05B12/08—Arrangements for controlling delivery; Arrangements for controlling the spray area responsive to condition of liquid or other fluent material to be discharged, of ambient medium or of target ; responsive to condition of spray devices or of supply means, e.g. pipes, pumps or their drive means
    • B05B12/085—Arrangements for controlling delivery; Arrangements for controlling the spray area responsive to condition of liquid or other fluent material to be discharged, of ambient medium or of target ; responsive to condition of spray devices or of supply means, e.g. pipes, pumps or their drive means responsive to flow or pressure of liquid or other fluent material to be discharged
    • B05B12/087—Flow or presssure regulators, i.e. non-electric unitary devices comprising a sensing element, e.g. a piston or a membrane, and a controlling element, e.g. a valve
    • B05B12/088—Flow or presssure regulators, i.e. non-electric unitary devices comprising a sensing element, e.g. a piston or a membrane, and a controlling element, e.g. a valve the sensing element being a flexible member, e.g. membrane, diaphragm, bellows
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B9/00—Spraying apparatus for discharge of liquids or other fluent material, without essentially mixing with gas or vapour
    • B05B9/03—Spraying apparatus for discharge of liquids or other fluent material, without essentially mixing with gas or vapour characterised by means for supplying liquid or other fluent material
    • B05B9/035—Spraying apparatus for discharge of liquids or other fluent material, without essentially mixing with gas or vapour characterised by means for supplying liquid or other fluent material to several spraying apparatus
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B08—CLEANING
    • B08B—CLEANING IN GENERAL; PREVENTION OF FOULING IN GENERAL
    • B08B3/00—Cleaning by methods involving the use or presence of liquid or steam
    • B08B3/02—Cleaning by the force of jets or sprays

Definitions

  • the invention relates to a device for the adjustable influencing of a fluid when it passes into the free space from a nozzle outlet, in particular a nozzle with adjustable jet geometry, comprising a first fluid line, at least one second fluid line, a swirl chamber, into which the first fluid line runs centrally in the axial direction and the at least one second fluid line entering a cylinder wall of the swirl chamber on a tangential plane at an entry angle deviating from an axial direction in order to generate a swirling flow which is oriented towards the nozzle outlet, with a first fluid flow in the first fluid line being in the axial direction flows towards a nozzle outlet and at least one second fluid flow in the at least one second fluid line on the cylinder wall enters the swirl chamber, the combination of both fluid flows in the swirl chamber causing different fluid flows depending on the difference between the volume flows of the first fluid flow and the second fluid flow Jet geometries emerge into the free space from the nozzle outlet connected to the swirl chamber, which can be varied between a linear full jet and a conical spray.
  • Hydraulic spray nozzles are used in many industrial processes, e.g. B. for cleaning, coating or cooling processes. Depending on the selected nozzle geometry, different jet shapes can be generated. While a full jet geometry generates a coherent full jet that enables large mechanical forces and mass flows in a small area, an atomizing nozzle can be used to create a droplet spray, hereinafter referred to as a spray, that wets a relatively large area in a short time. Atomizing nozzles usually have a geometry that causes an increase in turbulence and/or the creation of a swirl in the flow, so that a break-up of the jet can be induced as it leaves the nozzle exit.
  • Measures to increase the turbulence are, for example, strong flow deflection, abrupt cross-sectional changes or a collision of several partial flows near the nozzle outlet.
  • a swirl on the other hand, can be generated by swirl inserts or a flow introduced tangentially into a swirl chamber. Swirl atomization allows for more uniform sprays with smaller droplets than turbulence atomization.
  • Full jet nozzles on the other hand, are designed in such a way that the exiting full jet remains coherent over as long a distance as possible. This can e.g. B. be realized by streamlined nozzle geometries and avoiding abrupt cross-sectional changes.
  • jet shapes have different, sometimes conflicting properties
  • changing the jet shape as needed makes sense for processes with, in particular, changing process conditions and requirements in order to make the process efficient.
  • movable, z. B. rotating cleaning devices are used, for which a needs-based change in jet shape can be advantageous.
  • the nozzle outlet is designed to be variable in its cross section and thereby enables a variable atomization behavior when additional outlet geometries are opened or the area of the existing opening is changed.
  • a nozzle with a variable nozzle opening is more complex to produce, more prone to failure and places higher demands on the technical implementation and use in comparison to a nozzle with a fixed outlet opening. This involves increased effort in the hygienic design, maintenance, housing and complexity of the assembly.
  • the pamphlets DE 102 34 872 A1 and DE 101 49 981 A1 have two fluid lines, one of which is controllable, and which open into a swirl chamber from different angles.
  • the jet shape emerging from the nozzle is varied by alternating control, but also by the joint entry of the fluid from both fluid lines.
  • the axial and tangential entry of the fluid lines into the swirl chamber is also described (cf. DE 101 49 981 A1 , 2 , Paragraphs [0018]-[0021]), but the axial feed line and the swirl chamber have significant differences in diameter.
  • valves which are also designed as 3/2-way valves or 3/3-way valves, are required in order to achieve the change in jet shapes, at least in both cases there is no control over influencing the axial fluid line possible.
  • the jet only occurs when the tangential flow is blocked and the axially introduced fluid runs through the swirl chamber with as little disruption and turbulence as possible in order to leave the nozzle as a directed jet.
  • a superimposition of the axial flow with the tangential flow for jet generation, ie a change between spray and jet is not provided and only leads to a "mixed form" or in this case a relatively undisturbed superimposition of (hollow) cone spray and jet occurs and thus ultimately a full cone spray.
  • the latter is possible in particular when the swirl chamber is significantly larger than the axial orifice, since the tangential flow can flow around the axial flow on the wall of the swirl chamber relatively unhindered, without the swirl being reduced.
  • valves are used to affect fluid flow are from the references DE 102 59 563 A1 , DE 10 2007 054 673 B4 , EP 0 140 505 B1 , CN 206701530 UU , EP 2 059 347 B1 and DE 27 33 102 A1 known, also from the publications CN 108014935BB and DE 100 09 573 A1 .
  • valves are always arranged either in both partial flows, so that two valves are required, or one valve is used exclusively for influencing the cross flow, the bypass. This makes the design of one valve more complex.
  • control lines for signal transmission are often required or have to be operated manually. This will be in the pamphlets DE 100 09 573 A1 and EP 0 927 562 A2 disclosed.
  • the integration of control lines or the implementation of a manual adjustment require increased effort in their technical implementation. This applies in particular to technical systems that are mobile or rotating, that have higher requirements in terms of tightness (e.g. protection against water jets) or that are out of reach for manual intervention due to the process or for reasons of occupational safety.
  • a device for the adjustable influencing of a fluid as it passes into the free space from a nozzle outlet comprising a first fluid line, at least one second fluid line and a swirl chamber.
  • the first fluid line enters the swirl chamber centrally in the axial direction and the at least one second fluid line enters in a cylinder wall of the swirl chamber on a tangential plane at an entry angle deviating from an axial direction. This is done to create a swirling flow oriented toward the nozzle exit.
  • a first fluid flow flows in the first fluid line in the axial direction towards a nozzle outlet.
  • At least one second fluid flow enters the swirl chamber in the at least one second fluid line at the cylinder wall.
  • the combination of both fluid flows in the swirl chamber causes different jet geometries to exit into the free space from the nozzle outlet connected to the swirl chamber, depending on the difference between the volume flows of the first fluid flow and the second fluid flow.
  • the jet geometries can be varied between a linear full jet and a conical spray.
  • the cone-shaped spray emerges from the nozzle outlet as a full cone, with a hollow cone being provided according to an alternative embodiment.
  • the first fluid line has a valve for adjusting the volume flow of the first fluid flow that reaches the swirl chamber.
  • This makes it possible to control the jet shape with a single valve and to initiate the change between full jet and spray.
  • influencing the first fluid flow is sufficient to bring about the change between full jet and spray.
  • An additional influencing of the second fluid flow is not required.
  • the device according to the invention be designed as a compact and simple nozzle with a single valve.
  • the valve is also preferably designed as a simple 2/2-way valve that is sufficient for the desired function.
  • the diameter of the axial channel, the first fluid line is equal to the diameter of the swirl chamber and the cross section across the first fluid line and the swirl chamber, viewed in the axial direction, is constant.
  • the axial flow is not impeded and no geometry-related turbulences or pressure losses are generated during or until the axial flow enters the swirl chamber.
  • the cross sections of the first fluid line and the swirl chamber are different and have a diameter ratio, the ratio of the diameter of the first fluid line to the diameter of the swirl chamber, between 1.5 and 0.5, preferably between 1.3 and 0.7 or more preferably between 1.1 and 0.9.
  • the cross sections of the first fluid line and the swirl chamber are different, it is alternatively or additionally provided that the different cross sections of the first fluid line and the swirl chamber are connected via a flow-constant entry area with an angle of inclination ⁇ or ⁇ ′.
  • the consequence of this is that the first fluid flow does not separate from the wall in the case of a laminar flow type, but instead flows laminarly along the wall and thereby eliminates the swirl of the incoming second fluid flow particularly effectively and with little loss.
  • the value of the spray angle ⁇ is an indication of how much the swirl was reduced on the way through the nozzle under otherwise constant conditions (pressure, etc.): The smaller the angle at the exit, the more the swirl inside the nozzle was reduced.
  • the diameter ratio of the swirl chamber to the first fluid line or the flow-constant transition only have a swirl-reducing effect in jet operation, since the first fluid line is only open here.
  • the rest of the nozzle geometry can be designed favorably so that the swirl is hardly reduced and large spray angles are made possible when the spray emerges. As a result, it becomes possible to spray a large area and produce smaller, finer droplets that lead to better wetting behavior.
  • the full jet emerges from the nozzle outlet when the valve releases the first fluid line.
  • the spray emerges from the nozzle outlet when the valve blocks the first fluid line, so that only the at least one second fluid flow enters the swirl chamber.
  • the valve is applied in accordance with the fluid pressure that is present at the inlet of the valve on its side pointing towards the fluid connection. It works pressure-dependent and is either open in a first fluid pressure range in relation to a narrow switching point pressure or a wider transition range (to be assigned to the "first fluid pressure range") of the valve and closed in a second fluid pressure range or vice versa by being closed in the first fluid pressure range and in the second fluid pressure area is open.
  • a spray occurs at low pressures below the switching point pressure and a full jet at high pressures above the switching point pressure or vice versa.
  • the valve can be designed in such a way that it opens at the switching point pressure when the fluid pressure increases and closes when the fluid pressure falls below the switching point pressure, or vice versa.
  • An embodiment with a valve that always opens and closes at the same pressure, i.e. there is no hysteresis, and in which the valve starts at a first fluid pressure that is lower than the switching point pressure of the valve and in the entire first fluid pressure range is particularly preferred is closed while open from a second fluid pressure greater than the switch point pressure of the valve and throughout the second fluid pressure range.
  • the first fluid pressure or fluid pressure range is higher than the second.
  • a transition area with a partially closed valve is formed between the first fluid pressure area and the second fluid pressure area in place of the switching point.
  • a cone-shaped spray forms in the transition area.
  • the valve can be used in different versions, which are divided into different functional groups according to the type of preload (pneumatic, hydraulic, mechanical, inherent), the material properties of a closing body (elastic, rigid, compressible, incompressible) and the geometry (membrane-shaped, designed as a flap , slider, needle or cylinder) can be subdivided.
  • a combination of the functional groups enables a large number of embodiments of the valve.
  • the valve is designed as a pneumatically prestressed membrane valve which is filled with compressed air once before operation to determine a switching point pressure and is then sealed off.
  • a pneumatically prestressed membrane valve which is filled with compressed air once before operation to determine a switching point pressure and is then sealed off.
  • the valve is designed as a valve which is preloaded with a mechanical spring arrangement which acts on a rigid closing body (such as a flap, a slide, a needle or a cylinder).
  • a rigid closing body such as a flap, a slide, a needle or a cylinder.
  • an elastic closing body as z. B. embodies a membrane, are used.
  • a valve that is designed as a compressible, elastic body.
  • Other embodiments include rigid locking cylinders that are pneumatically preloaded, move and act as a valve.
  • the valve instead of a mechanical spring arrangement, the valve has a pair of permanent magnets that attract one another and act on a rigid or flexible closing body.
  • the fluid pressure p overcomes the magnetic force to open the valve, allowing the first fluid flow to pass through and into the swirl chamber.
  • the valve can also be designed with a single magnet interacting with a ferromagnetic material.
  • the magnet is preferably a permanent magnet because it is a very simple solution. Instead, however, an electromagnet can also be used.
  • the entry angle ⁇ of the second fluid line or of the second fluid is between 60° and 90° in relation to the axial direction.
  • the preferred swirl chamber is also designed to be flow-constant between the point at which the at least one second fluid line enters and the nozzle exit and without significant changes in geometry or cross-section that affect the flow and without abrupt changes. Accordingly, the cross section is essentially constant over the axial length of the swirl chamber.
  • the first fluid line and the at least one second fluid line result from at least one branch, in which a fluid flow entering the nozzle via the fluid connection is divided into partial flows, the first fluid flow and at least one second fluid flow.
  • the at least one branch is arranged in front of the valve, ie between the fluid connection and the valve. This means that only one fluid connection is necessary and there is no need for a number of fluid lines to be routed to the valve, which is also more compact and simpler in construction.
  • the first fluid line preferably has a larger cross section than the second fluid line.
  • the nozzle outlet can be designed as a known and commonly used solid jet nozzle outlet.
  • This component can therefore be installed in the device according to the invention as a standardized, inexpensive component without having to produce a special part for the nozzle outlet.
  • additional effects can be achieved with various different nozzle geometries.
  • Another suitable nozzle geometry has a cross section that tapers and then widens along a chamfer, similar to a counterbore, referred to below as the chamfer nozzle outlet.
  • the device is preferably designed as a cleaning nozzle and is provided for dispensing a cleaning liquid. As explained at the beginning, it is often necessary to change the jet shape during cleaning processes in order to be able to clean efficiently and with high effectiveness.
  • a nozzle arrangement which comprises at least two nozzles of the type described above.
  • a fluid enters this via a fluid connection which is at least fluidically connected to a supply line or alternatively via separate fluid connections with an adjustable fluid pressure in each supply line to one of the nozzles.
  • At least two of the nozzle devices are as described above and have valves, each with separately adjustable switching point pressures, which can also be set differently in order to to achieve the desired function.
  • the valves can be switched differently depending on the applied fluid pressure.
  • the output of the solid jet and the cone-shaped spray can be varied in such a way that all or part of the devices emit the linear solid jet or the spray.
  • a valve controlled by the pressure of the operating liquid, the fluid is used and several nozzles are connected to a pressure line, the fluid line.
  • valves are designed as pneumatically preloaded membrane valves, the different switching point pressures can be preset variably and as required and also changed later.
  • a further solution to the object of the invention consists in a method for operating a device for the adjustable influencing of a fluid when it passes into the free space from a nozzle outlet, as has been described above.
  • the procedure includes two different settings or process stages.
  • the linear full jet emerges in the first setting, in that the first fluid passes through the open valve and enters the swirl chamber together with the second fluid flow.
  • the influence of the second flow in the swirl chamber does not lead to the full jet being destroyed.
  • the collision of the fluid flows and the configuration of the nozzle geometry, in particular the taper in the nozzle outlet mean that the swirl introduced by the second fluid flow is greatly reduced in the subsequent nozzle section and the flow ultimately exits as a full jet.
  • An additional Influencing of the second fluid flow can therefore be omitted, which leads to a significant simplification.
  • the cone-shaped spray exits by preventing the first fluid flow through the closed valve from entering the swirl chamber and disturbing the formation of the swirl of the second fluid flow there.
  • the swirl experienced by the second fluid flow results in the formation of the spray as the desired jet shape at the nozzle outlet.
  • the closed valve opens at a switching point pressure when an opening pressure range is reached and the open valve is closed when the first fluid flow reaches a closing pressure range.
  • the intermediate range between the opening pressure range and the closing pressure range with the intermediate range defining the switching point pressure, the process of switching the valve from the closed position to the open position or vice versa takes place. Accordingly, the switching process takes place when an opening pressure range is reached or when a closing pressure range is reached, depending on the direction in which the fluid pressure changes. From reaching the opening pressure range, the valve is opened with increasing fluid pressure and vice versa, with decreasing fluid pressure, closed from reaching the closing pressure range. This applies when the cracking pressure range is above the closing pressure range, otherwise the behavior is reversed.
  • the first and the second adjustment of the jet shape are ultimately achieved via the control of the first fluid flow.
  • the intermediate range between the opening pressure range and the closing pressure range is very small, which is why the minimal hysteresis resulting from the intermediate range can be neglected and the small intermediate range can be regarded as the switching point.
  • a variant is preferred in which no hysteresis occurs and the closing pressure range directly borders the opening pressure range, so that the above-described switching point occurs, at which the switching process takes place.
  • the opening pressure range of the first fluid flow is above the closing pressure range or alternatively the closing pressure range is above the opening pressure range.
  • the first fluid flow advantageously has a higher volume flow than the second fluid flow. This can be realized at the crossing point of the lines when the flows enter the swirl chamber by choosing a suitable ratio of the line cross-sectional areas to one another.
  • a cross-sectional area of the first fluid line that is, for example, 2.5 times to 4.2 times larger than the added circular area of all second fluid lines or the tangential bores is particularly advantageous.
  • the self-pulsation is assumed to be triggered by a periodic blocking of the gas gap by the liquid film.
  • the phenomenon is also known for single-substance nozzles. Investigations focused in particular on spill-return or spillback nozzles, in which the fluid is introduced tangentially into a swirl chamber and part of the fluid via one or more axial Openings can flow back against the outflow direction from the swirl chamber. Strong pulsation can occur even if there is no axial opening. The cause is assumed to be that in these cases the air core, which forms inside the swirl chamber of such nozzles, becomes unstable under certain conditions and thus causes self-pulsation.
  • self-pulsation is regarded as a phenomenon to be avoided or as a useful one. If the focus is on atomization into the smallest possible droplets, it is not advisable to use pulsating sprays. If, however, a large-area, uniform wetting and the transfer of mechanical impact forces through the droplets to the surface being impacted are desired, self-pulsation is advantageous over non-pulsating sprays.
  • the pulsation generally occurs preferentially in the transition area.
  • the spray angle ⁇ of the spray without pulsation becomes increasingly smaller as the pressure increases, until the full jet is reached at a spray angle ⁇ of 0°.
  • the transition area there is a pulsating spray and a pulsating solid jet.
  • a pulsating spray is generated first and a further increase in pressure creates a pulsating full jet. This is caused by the approaching transition of the jet shape from spray to full jet.
  • there are periodic pressure fluctuations inside the nozzle (up to 0.3 bar), so that the switching pressure point is exceeded and a full jet is created, at least for a short time.
  • the non-pulsating, clearly recognizable jet is always designated as the full jet and the associated fluid pressure as the switching point pressure, which allows the transition to the jet area to be recognized.
  • the pulsating jet that occurs in the transition area is associated with the first fluid pressure range since the transition range is a sub-range of the first fluid pressure range.
  • the range of fluid pressure in which self-pulsation occurred depends on the nozzle geometry, in particular the diameter of the nozzle exit and the ratio of the summed cross-sectional areas of all second fluid lines to the cross-sectional area of the first fluid line. Furthermore, the preload of the valve has an impact on the range of fluid pressure in which self-pulsation occurs.
  • the nozzle presented can be designed differently depending on the process requirements. Either the nozzle is designed so that it does not have a range of fluid pressure in which self-pulsation occurs, so that when the valve is closed only a non-pulsating spray is produced and when the valve is open a solid jet is produced. Or the nozzle is designed to have one or more ranges of fluid pressure in which self-pulsation occurs such that when the valve is closed a non-pulsating or a pulsating spray is produced depending on the operating pressure and when the valve is open a solid jet is produced.
  • the use of a pulsating spray can offer advantages over a continuous spray, since some types of dirt typical of industry can be demonstrably cleaned more efficiently if the liquid hits the surface to be cleaned discontinuously.
  • continuous sprays there is no stationary film flow on the exposed surface, but the amount of fluid flows off to the side after impacting the soiled surface.
  • the amount of fluid that follows hits the dirt directly and undamped, thereby enabling the transmission of larger impact forces.
  • the droplets which are on average larger than non-pulsating sprays, also enable the transfer of increased impulses to the dirt.
  • the nozzle according to the invention enables an adjustable change between the jet forms “spray” and “full jet” even without pulsation effects, in order to be able to use the respective jet form as required.
  • the opening at the nozzle exit remains unchanged in terms of area and geometry, but both spray and full jet can exit.
  • the switching of the nozzle between the jet forms is controlled solely by the pressure of the fluid, the operating fluid (e.g. water or cleaning fluid), so that no additional control lines are necessary.
  • the nozzle In parallel operation with several nozzles of the same type, the nozzle also allows hybrid operation of full jet and spray, especially when one of the pressure of the Operating fluid-controlled valve is used and the switching pressures of the individual nozzles are set differently, so that more than just two operating modes for the entire system can be set as required.
  • the preferred embodiment of the valve enables pressure-controlled switching.
  • the intermediate range between the opening pressure range and the closing pressure range, in which the switchover between open and closed valve takes place, or the switching point when the switchover between open and closed valve takes place hysteresis-free with practically no intermediate range worth mentioning, is determined by the geometric parameters of the nozzle or the preload of the spring element or by means of pneumatic pressure. After a one-off setting, reliable and repeatable switching takes place.
  • the nozzle Due to the possibility of switching the jet shape by adjusting the pressure of the operating liquid, the nozzle can easily be retrofitted to existing devices.
  • the desired switching pressure can be set very easily by changing the preload of the valve or the nozzle geometry (e.g. nozzle diameter) once. After that, switching is always reliable and repeatable at the same switching point pressure.
  • atomization when generating the spray is based on a swirling flow
  • similar atomization properties can be generated as with industrial, also swirl-based full cone nozzles or hollow cone nozzles. Uncontrolled atomization or pressure losses, as with atomization due to the collision of two flows, are thus avoided.
  • Known nozzles usually emit a spray that has the shape of a hollow cone.
  • the spray regularly has the shape of a full cone, with the result that the entire surface is wetted evenly overall.
  • the shape of a hollow cone can also be aimed at, if this is desired.
  • a hollow cone is achieved by making the cross section of the tangential flow very small or the taper at the nozzle exit very short, which would correspond to the design guidelines for hollow cone nozzles. Fundamentally allows a hollow cone opposite a full cone atomizes the spray into even smaller droplets because there is more opportunity for the droplets to interact and rub with the surrounding air. It is also planned to use appropriately designed nozzles to switch between the hollow cone and the solid jet, in order to combine the advantages of both jet shapes and use them alternately.
  • Parallel operation with several nozzles, each of which has different switching points, enables other operating states in addition to spray and full jet, in which spray and full jet are generated simultaneously with different nozzles (hybrid operation).
  • the pressure line for supplying the fluid is necessary in order to set the desired operating state in a targeted manner. This allows many new applications for an overall system in which the nozzles are embedded.
  • Another advantage lies in the fact that there is only one nozzle outlet, the geometry of which cannot be changed.
  • the jet axes of both jet forms are identical, so that no relative displacement between the system and the aimed local target has to be made and calculated, as is the case when a local target is to be hit successively with both jet forms of a nozzle. If a valve that opens at high pressure is used, a spray can be generated at low operating pressure and a full jet at high operating pressure. This has particular advantages for processes in which large mechanical forces are to be transmitted with the solid jet. This primarily includes cleaning processes.
  • FIG. 1 shows schematically a longitudinal section view of an embodiment of a nozzle 1 according to the invention with a transverse section detail, the section AA, and a longitudinal section detail, the section from frame B, which illustrates what is happening in the swirl chamber 6 of the nozzle body 2.
  • the representation was made appropriately for simplification and for a better overview of all essential lines in deviation from a standard representation by a second fluid line 10 being shown in section in the view on the left, although it is not in the centrally selected sectional plane.
  • a swirl chamber 6 with a central section would also not show the vertical section of the second fluid line 10 in section, but only the opening of its entry into the swirl chamber 6, which would have an oval contour due to the tangential entry point when penetrating the wall of the swirl chamber 6 .
  • the nozzle 1 includes a fluid port 3, which is the interface to the upstream device such. B. a tank cleaner or a robot, and a nozzle outlet 4, from which the fluid flows out in the desired jet shape 30, 32, as well as a branch 16 for dividing the fluid flow into two partial flows and a combination in the swirl chamber 6 for the partial flows to flow together again.
  • a fluid port 3 which is the interface to the upstream device such. B. a tank cleaner or a robot, and a nozzle outlet 4, from which the fluid flows out in the desired jet shape 30, 32, as well as a branch 16 for dividing the fluid flow into two partial flows and a combination in the swirl chamber 6 for the partial flows to flow together again.
  • the first fluid flow 12 runs approximately axially to the main flow direction along the axis direction 9
  • another partial flow, the second fluid flow 14, at the branching 16 and the merging in the swirl chamber 6 is not axial to the main flow direction, here aligned perpendicularly is.
  • the area between the merging of the fluid flows 12, 14 in the swirl chamber 6 and the nozzle outlet 4 is preferably designed to be approximately constant in flow, without sudden changes in geometry, and preferably has a constant cross-section over the entire course until the taper is reached near the nozzle outlet 4 in the axial direction 9 on. In the case of laminar flow, the flow does not detach from the wall and remains laminar. Even for cross sections of the first fluid line 8 and the swirl chamber 6 that differ from one another, a flow-constant entry region 7 is preferably implemented, via which the first fluid flow 12 enters the first fluid line 8 into the swirl chamber 6 in laminar flow without detaching from the wall.
  • the entry area 7 has an angle of inclination ⁇ , ⁇ ′ which is selected as a function of the rheological parameters, above all the flow rate of the first fluid flow 12, so that the laminar flow maintains the laminar state.
  • valve 20 Located between the branch 16 and the swirl chamber 6 in the first fluid line 8 is a valve 20 with which the axial partial flow, the first fluid flow 12, can either be blocked or switched through.
  • the valve 20 preferably opens and closes as a function of a set constant preload and as a function of the fluid pressure of the operating liquid, the fluid.
  • the nozzle outlet 4 can be designed as a commercial full jet nozzle outlet, so that available Purchased parts can be used to z. B. to be able to adjust the nozzle diameter very easily by retrofitting and using a different nozzle.
  • the nozzle outlet 4 which is preferably designed as a full jet nozzle outlet, is arranged on the nozzle body 2, and the nozzle body 2 also has a first fluid line 8, in which the valve 20 is inserted, and a second fluid line 10, which bridges the valve 20.
  • the fluid flow entering the nozzle 1 at the fluid connection 3 is divided at the branch 16 and a part flows via the second fluid line 10 until it enters the swirl chamber 6.
  • the second fluid line 10 enters at the entry angle ⁇ , which is 90° in the illustrated embodiment ° is, in the area of the cylinder wall of the cylindrical swirl chamber 6 a.
  • the valve 20 If the valve 20 is closed, the entire volume flow of the incoming fluid flow flows via the second fluid line 10. Since the second fluid line 10 enters the swirl chamber 6 in the area of a tangential surface, the entering second fluid flow 14 receives a twist, it flows around the Axis 9. On the tangential surface, the entry angle ⁇ is preferably set between 60° and 90°. The fluid retains its swirl when it progresses out of the swirl chamber 6 to the nozzle outlet 4 and leaves the nozzle outlet 4 there in the form of a conical spray 30 . However, as soon as the valve 20 is opened, the swirl of the second fluid flow 14 is influenced or disturbed by the first fluid flow 12 also entering the swirl chamber 6 . The jet pattern leaving the nozzle outlet 4 changes, as again in the following 2 explained in more detail.
  • FIG. 2 shows schematically a longitudinal section view of an embodiment of a nozzle 1 according to the invention with two different positions of the valve 20 and the resulting jet shapes, the conical spray 30 and the full jet 32.
  • the full jet 30 according to the illustration above results when the valve 20 is closed, which means that there is no flow can enter the swirl chamber 6 in the axial direction.
  • the entire volume flow of the fluid is set into a swirl and generates the conical spray 30 with a spray angle ⁇ when it exits the nozzle outlet 4 .
  • the lower illustration shows the open valve 20 through which the first fluid flow 12 enters the swirl chamber 6 and influences the swirl of the second fluid flow 14 there in such a way that a full jet leaves the nozzle outlet 4 .
  • closing body of the valve 20 are a flexible, elastic membrane, a compressible closing body, a rigid closing body (e.g. flaps, sliders, needles, cylinders) or an elastic closing body, each in connection with a prestress.
  • the valve mechanism is designed for repeatable and reliable opening and closing.
  • the range of fluid pressure also referred to as fluid pressure range
  • fluid pressure range in which switching takes place is very small and can therefore practically be ignored as a range, so that one can speak of a switching point or switching point pressure in relation to the entire working pressure range.
  • the closing body of the prestressed diaphragm valve 22 is designed as an elastic diaphragm 21, with the prestressing being achieved by means of compressed air. This structure allows a simple design of the switching behavior for the industrial application of the nozzle 1.
  • FIG. 3 shows schematically a longitudinally sectioned view of an embodiment of a nozzle 1 according to the invention with two different positions of a valve 20 with a prestressed membrane body 22 and the resulting jet shapes.
  • the valve 20 is closed, in which the membrane body 22 was charged with compressed air via a compressed air supply 23 .
  • the first fluid line 8 is closed and all of the fluid that enters the nozzle 1 flows via the second fluid line 10 into the swirl chamber 6, where it is swirled and leaves the nozzle outlet 4 as a conical spray 30.
  • the valve 20 opens and the first fluid line 8 opens.
  • the fluid line 8 which is larger than the second fluid line 10 , thus disrupts the formation of the swirl in the swirl chamber 6 , with the result that a full jet is produced at the nozzle outlet 4 .
  • a space filled with compressed air can also be provided as a compressed air reservoir, the initial air pressure of which is only changed to change the operating point before the nozzle 1 is operated and remains sealed off during operation.
  • the diaphragm valve 22 is controlled by the pressure of the fluid entering the nozzle. At a high fluid pressure p it opens, as soon as the fluid pressure p decreases below the set operating point, the membrane valve 22 (like any other valve 20 used with a preload) closes again, as shown in the illustration on the left.
  • Figure 4a shows schematically a longitudinal section view of a further embodiment of a nozzle 1 according to the invention with a spring valve 24, with two different valve positions of the spring valve 24 being shown, and the resulting jet shapes, conical spray 30 and full jet 32.
  • a spring 25 is used here, the force of which determines the operating point of the prestressed spring valve 24 .
  • the axial first fluid flow 12 enters the swirl chamber 6 and generates the full jet 32 at the nozzle outlet 4. If the fluid pressure p falls below the operating point of the spring valve 24, then the spring valve 24 and closes the fluid flow takes its way as a second fluid flow 14 via the second fluid line 10 into the swirl chamber 6, where the swirl caused thereby leads to the exit of a conical spray 30.
  • magnetic force is used instead of the spring force, which in the illustrated embodiment is caused and implemented as two mutually attracting magnets, a pair of permanent magnets 29.
  • the fluid pressure p overcomes the magnetic force to open the valve 20, so that the first fluid flow 12 can enter the swirl chamber 6.
  • a pair of permanent magnets 29 a single magnet can also be provided in interaction with a ferromagnetic material, with the permanent magnet being a very simple solution, but an electromagnet can also be used instead.
  • the magnet-driven valve 20 is preferably designed in such a way that a flexible membrane or the like is prestressed by two magnetic bodies which are arranged in such a way that they attract each other, in particular due to their polarity, so that the first fluid line 8 is closed . As soon as the first fluid flow 12 reaches a higher pressure, the magnetic force is overcome and the valve opens.
  • the valve is embodied as a "high pressure opening valve”.
  • FIG 5 shows schematically a longitudinally sectioned view of an alternative embodiment of a nozzle 1 according to the invention with two different valve positions of a valve with a compressible valve body 26 and the resulting jet shapes, conical spray 30 and full jet 32, as also in FIGS Figures 2 to 4 shown.
  • a compressible elastic valve body 26 closes against the pressure of the first fluid flow 12 in the first fluid line 8 and thereby blocks it. If, on the other hand, the fluid pressure p exceeds the working point of the valve 20 against the force of the elastic valve body 26, the valve 20 opens and the full jet 32 emerges from the nozzle outlet 4 after the first fluid flow 12 has flown through the swirl chamber 6 axially.
  • FIG. 6 shows schematically three longitudinally sectioned views of an embodiment of a nozzle 1 according to the invention in a double arrangement with a common fluid supply for both nozzles 1.
  • Two nozzles are connected to the same pressure line.
  • the same pressure p is applied to both nozzles.
  • the two valves 20 have different operating points, so that a variable jet pattern can be achieved at the two nozzles 1 (nozzle A and nozzle B).
  • the pressure line which carries the fluid entering the nozzle, also serves as a control line, so that several states can be implemented very flexibly and easily with just one signal (pressure of the fluid).
  • the pressure p at the entrance to the two nozzles 1 is in the closing pressure range, so that both valves 20 are closed and all of the fluid in enters the two swirl chambers 6 via the second fluid line 10 and generates the conical spray 30 in both nozzles 1 .
  • the pressure p is chosen so that it is in the opening pressure range for one of the nozzles 1 and opens the valve 20, but remains closed for the other. As a result, a full jet 32 and a cone-shaped spray 30 emerge.
  • valve 20 can be used which is closed at low pressure and open at high pressure.
  • an inverse characteristic can also be provided, in which the valve is closed at high pressure and open at low pressure.
  • the parallel operation is z. B. is particularly important for container cleaning.
  • Several nozzles 1 are operated in parallel on a rotating cleaning device that has only one pressure line.
  • FIG. 7 shows schematically four longitudinal section views of an embodiment of a nozzle 1 according to the invention in a double arrangement with a separate fluid supply, which differs from the illustration from 6 has the consequence that the spray pattern can be set individually for both nozzles 1, depending on the fluid pressure with which the fluid hits the nozzle 1.
  • the fluid pressure p 1 is identified as a low fluid pressure and the fluid pressure p 2 as a high fluid pressure, in each case in relation to the operating point of the valve 20 .
  • an alternative embodiment provides for the valve 20 to be closed at high pressure and open at low pressure.
  • State 1 shows the low fluid pressure p 1 for both nozzles 1, which is below the operating point of the valve 20, so that the latter remains closed. The result is cone-shaped sprays 32 at both nozzle outlets 4.
  • the left-hand nozzle 1 receives the higher fluid pressure p 2 so that the valve 20 allows the fluid flow to pass axially and a full jet 32 is produced at the nozzle outlet 4, while the right-hand nozzle 1 continues to deliver the spray 30 with the valve 20 closed.
  • state 3 this is exactly the opposite with respect to state 2; the pressure conditions at the entrance of the two nozzles 1 are reversed.
  • the higher fluid pressure p 2 is present at both nozzles 1, the valve opens and both nozzles emit the full jet 32.
  • the full jet nozzle outlet 4 is a standard component that is easily and inexpensively available.
  • the solid jet 32 emerges from the nozzle outlet 4 (cf. Figures 2 to 7 ) off when valve 20 (cf. Figures 1 to 7 ) the first fluid line 8 releases.
  • the spray 30 emerges from the nozzle outlet 4 when the valve 20 blocks the first fluid line 8 , so that only the at least one second fluid flow 14 enters the swirl chamber 6 .
  • FIG. 11 shows a sectional side view with details A(1) to A(5), the variants of the transition from the first fluid line 8 to the swirl chamber 6, and 12 shows a view from above of an embodiment of a nozzle 1 according to the invention.
  • the fluid connection 3, where the fluid enters, can be seen on the left side of the nozzle body 2, followed in the direction of flow (arrow) by the branch 16 at which the fluid flows between the first fluid line 8 and the second fluid line 10 splits.
  • a push-in fitting 17 is provided for this purpose, with which the second fluid line 10 is inserted on the nozzle body 2 .
  • the second fluid line 10 is designed as a media hose 11 until it re-enters the nozzle body 2 in the area of the swirl chamber 6 by means of a further push-in screw connection 17 .
  • the nozzle outlet 4 is attached to the right-hand side of the nozzle body 2 and, in the preferred embodiment shown here, is designed as a full jet nozzle that is available as standard.
  • an inlet area 7 is provided between the first fluid line 8 and the swirl chamber 6, via which the first fluid flow from the first Fluid line 8 enters the swirl chamber 6 and its function already 1 was executed.
  • the ratio of the diameter D8 of the first fluid line 8 to the diameter D6 of the swirl chamber 6 is shown as detail variant A(1) at 0.7 in the Detail variants A(2) and A(4) and 1.3 shown in detail variants A(3) and A(5).
  • Diameter D8 and diameter D6 are also indicated in detail variant A(1), which has been omitted in the other representations of detail variants A(2) to A(5) and also in the associated description for the sake of a better overview.
  • the design of the transition to A(1) to A(5) favors an effective superimposition of the first fluid flow with the second fluid flow in the swirl chamber.
  • the first fluid flow 12 has predominantly axial velocity components and flows through the cross section of the swirl chamber 6 as a core flow primarily in the center, coaxially to the nozzle axis, the axis of symmetry of the nozzle 1, while the second fluid flow 14 has predominantly radial velocity components and the cross section of the swirl chamber 6 primarily at the outer edge area flows radially in a circular path.
  • An "effective superimposition" of the fluid flows 12, 14 is characterized in that the axial velocity components of the first fluid flow 12 reduce the radial velocity components of the second fluid flow 14 sufficiently so that the resulting twist in the combined fluid flow (due to e.g.
  • the fluid flows 12, 14 are also effectively superimposed if the entry area 7 is designed as a small jump with a ratio of the diameter of the first fluid line 8 to the diameter of the swirl chamber 6, the ratio being as shown in detail variant A(2) by way of example , is 0.7 or, as shown in detail variant A(3), is 1.3.
  • the cross section of the first fluid line 8 is smaller in comparison to the swirl chamber 6, after the first fluid flow 12 enters the swirl chamber 6, flow separation and vortices are formed.
  • the axial velocity components of the first fluid flow 12 therefore no longer penetrate the cross section of the swirl chamber 6 in the area of separation as effectively as they did in the first fluid line 8 , but are somewhat weakened in the edge region of the swirl chamber 6 .
  • the area on which the first and second fluid flows 12, 14 overlap and an interaction of axial and radial velocity components takes place is somewhat reduced in terms of effective interaction compared to detail view A(1), but is still effective enough to reduce the swirl so to reduce far that this can be completely eliminated up to the nozzle outlet 4 (due to z.
  • the effectiveness of the overlay can be increased by e.g. B.
  • the swirl chamber 6 is lengthened in the area between the inlet region 7 and the junction to such an extent that the first fluid flow 12 rests against the wall of the swirl chamber 6 until it overlaps with the second fluid flow 14 .
  • the first fluid flow 12 with its axial velocity components penetrates the swirl chamber 6 in the entire cross section without weakening in the edge region due to separation and can superimpose the radial velocity components of the second fluid flow 14 in the edge region of the swirl chamber 6 over a large area and very effectively.
  • the cross section of the first fluid line 8 is larger in comparison to the swirl chamber 6, flow separation and vortex formation occur before the first fluid flow enters the swirl chamber.
  • the separation area extends into the swirl chamber 6 .
  • the axial velocity components of the first fluid flow 8 no longer penetrate the cross section of the swirl chamber 6 in the region of the separation as effectively as in the first fluid line 8 before the separation, but are somewhat weakened in the edge region of the swirl chamber 6 .
  • the area on which the first and second fluid flows 12, 14 overlap and an interaction of axial and radial velocity components takes place is somewhat reduced in terms of effective interaction compared to detail view A(1), but is still effective enough to Swirl to reduce so far that this can be completely eliminated up to the nozzle outlet 4 (by z. B. wall friction) and a full jet 32 exits.
  • the effectiveness of the overlay can be increased by e.g. B. the swirl chamber 6 is lengthened in the area between the inlet region 7 and the junction to such an extent that the first fluid flow 12 rests against the wall of the swirl chamber 6 until it overlaps with the second fluid flow 14 .
  • the first fluid flow 12 with its axial velocity components penetrates the swirl chamber 6 in the entire cross section without weakening in the edge region due to separation and can superimpose the radial velocity components of the second fluid flow 14 in the edge region of the swirl chamber 6 over a large area and very effectively.
  • a ratio of 0.7 to 1.3 of the diameter of the first fluid line 8 to the diameter of the swirl chamber 6 is particularly recommended when the diameter of the nozzle outlet 4 is between 0.85 and 3.2 mm and the ratio of the cross-sectional area of the first Fluid line 8 to cross-sectional area of all second fluid lines 14 combined is between 1.2 to 7.0.
  • An effective superimposition of the fluid flows 12, 14 can also be realized with an entry region 7, which is designed according to the detail variants A(4) and A(5).
  • the inlet area 7 is designed to be flow-constant, in that the transition from the first fluid line 8 to the swirl chamber 6 is designed via the angle of inclination ⁇ (decreasing towards the swirl chamber 6) or ⁇ ′ (decreasing towards the first fluid line 8, therefore increasing towards the swirl chamber 6). .
  • the inclined transition avoids detachment of the fluid flow 12 and in the case of a laminar flow kept them in the laminar state.
  • a laminar and non-viscous flow flows through a cross-sectional enlargement or a diffuser (the swirl chamber 6) without separation from the wall and the angle of inclination is sufficiently flat, there are no vortices or hardly any friction losses due to turbulence.
  • the design of a diffuser is known per se from the prior art.
  • the opening angle is a key figure for the broadening of the flow cross section of the diffuser. For centrifugal pumps, the critical value is usually around 8° to 10°. If the opening angle is too large (supercritical diffuser), dissipation occurs due to the flow detaching from the diffuser wall, which leads to strong turbulence in the transition areas to the dead spaces.
  • the detailed variant A(4) shows a gradual enlargement of the cross section in the entry area 7, in which the axial velocity components decrease as the cross section enlarges.
  • the detailed variant A(5) shows a gradual narrowing of the cross section in the entry area 7, in which the axial velocity components increase as the cross section decreases.
  • the axial velocity components of the first fluid flow 12 which are pronounced throughout the cross section of the swirl chamber 6 , therefore superimpose the radial velocity components of the second fluid flow 14 in the edge region of the swirl chamber 6 over a large area and very effectively.
  • detail variant A(2) is actually executed in the overall representation of the nozzle 1
  • detail variants A(1), A(3), A(4) and A(5) can be used as alternatives take their place in each case and take their place depending on the requirement.
  • Requirements can be, for example, a short installation space for the nozzle or a low pressure drop.
  • valve 20 Arranged centrally in the nozzle body 2 is the valve 20 which, in the preferred embodiment shown, has a diaphragm sleeve 28 and the diaphragm 21 .
  • the valve 20 is held by a nozzle fitting 3 which joins the two parts of the nozzle body 2 together.
  • a sealing ring 5 is inserted between the nozzle screw connection 3 and the nozzle body 2 .
  • the nozzle also has a non-return valve 18 which is also connected to the nozzle screw connection 3 via a push-in screw connection 17 .
  • the check valve 18 is used for tool-free rapid filling of the valve with a gas such. B. compressed air, without this flowing back (locking function). Filling with compressed air is possible without tools, for venting a vent screw (not shown) is provided on the opposite side of the nozzle screw connection.

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EP22214712.6A 2021-12-17 2022-12-19 Buse à géométrie de faisceau réglable, ensemble buse et procédé de fonctionnement d'une buse Pending EP4197643A1 (fr)

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DE102021133674.0A DE102021133674A1 (de) 2021-12-17 2021-12-17 Düse mit einstellbarer Strahlgeometrie, Düsenanordnung und Verfahren zum Betrieb einer Düse

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GB720859A (en) 1952-03-31 1954-12-29 Paul Lechler Improvements in or relating to nozzles for jet pipes and the like
US3746262A (en) 1971-10-12 1973-07-17 Bete Fog Nozzle Inc Spray nozzle
DE2733102A1 (de) 1977-07-22 1979-02-01 Bayer Ag Verfahren und vorrichtung zum zerstaeuben von fluessigkeiten
EP0121877B1 (fr) 1983-04-06 1988-11-02 BASF Aktiengesellschaft Buse de pulvérisation en forme d'un cône creux
EP0140505B1 (fr) 1983-08-15 1989-03-15 Generale de Mecanique et Thermique Procédé de nettoyage d'éléments industriels et système de jet pour la mise en oeuvre de ce procédé
DE4324731A1 (de) 1992-07-23 1994-01-27 Spraying Systems Co Selbstreinigende Sprühdüse
EP0724913A2 (fr) 1995-02-03 1996-08-07 Carl Leopold Clarence Kah, Jr. Buse de pulvérisation à arc de pulvérisation réglable
EP0927562A2 (fr) 1998-01-05 1999-07-07 Vigh, Andreas, Dipl.-Ing. (FH) Génération de jet plat par buse d'éjection creuse pour la lutte contre les incendies
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DE10234872A1 (de) 2002-07-31 2004-02-19 Valeo Auto-Electric Wischer Und Motoren Gmbh Steuerventil, Düsenanordnung und Waschanlage
DE10259563A1 (de) 2002-12-19 2004-07-01 Valeo Systèmes d`Essuyage Waschdüse zur Verwendung an Fahrzeugen zum Ausbringen eines flüssigen Reinigungs- oder Waschmediums
DE102005013127B4 (de) 2004-11-12 2007-08-23 Aweco Appliance Systems Gmbh & Co. Kg Sprühvorrichtung zum Versprühen einer Betriebsflüssigkeit
DE102007054673B4 (de) 2007-11-14 2009-09-24 Jürgen Löhrke GmbH Bandschmiereinrichtung und/oder Reinigungs-Desinfektionsanlage
EP2059347B1 (fr) 2006-08-23 2010-08-04 Valiant Corporation Ensemble de buse a impulsion haute pression
EP2441522A2 (fr) 2010-10-14 2012-04-18 Lechler GmbH Buse destinée à atomiser un fluide
EP1885910B1 (fr) 2005-05-12 2013-04-03 Spraying Systems Co. Systeme de pulverisation destine a la pulverisation progressive d'objets non rectangulaires
DE102016203769A1 (de) 2016-03-08 2017-09-14 Mahle International Gmbh Flüssigkeitsnebelabscheideeinrichtung
CN206701530U (zh) 2017-04-09 2017-12-05 南京林业大学 喷雾射流多功能喷头
CN108014935A (zh) 2017-11-08 2018-05-11 江苏苏美达五金工具有限公司 一种压力线性调节组合喷嘴及高压清洗设备

Patent Citations (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB720859A (en) 1952-03-31 1954-12-29 Paul Lechler Improvements in or relating to nozzles for jet pipes and the like
US3746262A (en) 1971-10-12 1973-07-17 Bete Fog Nozzle Inc Spray nozzle
DE2733102A1 (de) 1977-07-22 1979-02-01 Bayer Ag Verfahren und vorrichtung zum zerstaeuben von fluessigkeiten
EP0121877B1 (fr) 1983-04-06 1988-11-02 BASF Aktiengesellschaft Buse de pulvérisation en forme d'un cône creux
EP0140505B1 (fr) 1983-08-15 1989-03-15 Generale de Mecanique et Thermique Procédé de nettoyage d'éléments industriels et système de jet pour la mise en oeuvre de ce procédé
DE4324731A1 (de) 1992-07-23 1994-01-27 Spraying Systems Co Selbstreinigende Sprühdüse
EP0724913A2 (fr) 1995-02-03 1996-08-07 Carl Leopold Clarence Kah, Jr. Buse de pulvérisation à arc de pulvérisation réglable
EP0927562A2 (fr) 1998-01-05 1999-07-07 Vigh, Andreas, Dipl.-Ing. (FH) Génération de jet plat par buse d'éjection creuse pour la lutte contre les incendies
DE10009573A1 (de) 2000-02-29 2001-08-30 Mabo Steuerungselemente Vertri Düseneinrichtung, vorzugsweise angeordnet in sanitären Wasserbecken, Behältern oder dergleichen
DE10149981A1 (de) 2001-10-10 2003-05-08 Valeo Auto Electric Gmbh Düsenanordnung für eine Waschanlage für Fahrzeugscheiben sowie Waschanlage mit einer solchen Düsenanordnung
DE10234872A1 (de) 2002-07-31 2004-02-19 Valeo Auto-Electric Wischer Und Motoren Gmbh Steuerventil, Düsenanordnung und Waschanlage
DE10259563A1 (de) 2002-12-19 2004-07-01 Valeo Systèmes d`Essuyage Waschdüse zur Verwendung an Fahrzeugen zum Ausbringen eines flüssigen Reinigungs- oder Waschmediums
WO2004056489A1 (fr) 2002-12-19 2004-07-08 Valeo Systemes D'essuyage Buse de lavage pour produire un jet de liquide de nettoyage ou de lavage
DE102005013127B4 (de) 2004-11-12 2007-08-23 Aweco Appliance Systems Gmbh & Co. Kg Sprühvorrichtung zum Versprühen einer Betriebsflüssigkeit
EP1885910B1 (fr) 2005-05-12 2013-04-03 Spraying Systems Co. Systeme de pulverisation destine a la pulverisation progressive d'objets non rectangulaires
EP2059347B1 (fr) 2006-08-23 2010-08-04 Valiant Corporation Ensemble de buse a impulsion haute pression
DE102007054673B4 (de) 2007-11-14 2009-09-24 Jürgen Löhrke GmbH Bandschmiereinrichtung und/oder Reinigungs-Desinfektionsanlage
EP2441522A2 (fr) 2010-10-14 2012-04-18 Lechler GmbH Buse destinée à atomiser un fluide
DE102016203769A1 (de) 2016-03-08 2017-09-14 Mahle International Gmbh Flüssigkeitsnebelabscheideeinrichtung
CN206701530U (zh) 2017-04-09 2017-12-05 南京林业大学 喷雾射流多功能喷头
CN108014935A (zh) 2017-11-08 2018-05-11 江苏苏美达五金工具有限公司 一种压力线性调节组合喷嘴及高压清洗设备

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