EP3523543A1

EP3523543A1 - Fluidic component

Info

Publication number: EP3523543A1
Application number: EP17787354.4A
Authority: EP
Inventors: Jens WINTERING; Bernhard BOBUSCH; Oliver Krueger
Original assignee: FDX Fluid Dynamix GmbH
Current assignee: FDX Fluid Dynamix GmbH
Priority date: 2016-10-06
Filing date: 2017-10-05
Publication date: 2019-08-14
Also published as: US20200038884A1; DE102016219427A1; WO2018065533A1; CN109863315A

Abstract

The invention relates to a fluidic component (1) for producing a free jet (15), wherein: the component (1) has a flow chamber (10) through which a fluid stream (2) can flow, said fluid stream enters the flow chamber (10) through an inlet opening (101) and exits the flow chamber (10) through an outlet opening (102), the flow direction of said fluid stream runs substantially parallel to the main extension direction of the flow chamber (10), and a main flow channel (103) and secondary flow channels (104) are located inside the flow chamber (10), characterised in that the cross-sectional profile of the main flow channel (103), in the main extension direction of the flow chamber (10), is divergent over the entire length of the main flow channel (103) or is divergent in some sections and convergent in some sections. Additionally or alternatively, a component (1) is also claimed with an exit region (108) which is free of obstructions downstream of the outlet opening (102).

Description

Fluidic component

The invention relates to a fluidic component according to claim 1, a fluidic component according to claim 15, a device comprising such a fluidic component having the features of claim 29.

The fluidic component is provided for generating a moving fluid jet. Examples of such fluid flow patterns are, beam oscillations, rectangular, sawtooth or triangular beam paths, spatial or temporal jet pulsations and switching operations. Oscillating fluid jets are used, for example, to evenly distribute a fluid jet (or fluid stream) to a target area. The fluid stream may be a liquid stream, a gas stream or a multiphase stream (for example, wet steam).

Fluidic components, for example from US Pat. No. 8,702,020 B2, are known from the prior art for producing a moving fluid jet. So far, these fluidic components are used without appreciable divergent proportion, since the beam quality from the outlet of the component, e.g. does not matter for flow control. In addition, the oscillation angle or also known as spray angle, previously limited to an angle of less than 60 ° and also plays the temporal beam path, which is responsible for the fluid distribution, a minor role.

The invention thus relates to fluidic components which have an increased beam quality and or generate a larger oscillation angle and or have a more uniform fluid distribution. This is achieved on the one hand by a divergent proportion to increase the beam quality and / or on the other to influence the spray angle. In addition, with the invention, an oscillation angle of about 60 ° to 160 ° is possible. By beam quality is meant here as long as possible a compact oscillating fluid jet. So far, attempts are made to burst the exiting fluid jet as quickly as possible in order to thus generate the largest possible spray angle and or to generate the smallest possible droplets, as is performed, for example, with interfering elements in the flow guidance, as is known from US Pat. No. 5,035,361 A.

For generating a movable fluid flow (or fluid jet) further fluidic components are known. The fluidic components do not include any movable components that serve to generate a motile fluid flow. This shows them in comparison to the prior art nozzles not on the disadvantages resulting from the moving components.

The present invention has for its object to provide a fluidic component which is designed, a movable fluid jet preferably with a high spray angle.

These fluidic components can be used in different devices in which hitherto nozzles are used. Typical devices are in agriculture, for example, in sprayers for liquid fertilizers or, for example, for pesticides or irrigation systems. Other typical devices in which the fluidic components are used are cleaning devices or systems, such as dishwashing devices, dishwashers, belt transport washers, industrial Teilereinigungsanlangen, Abspülgeräte, high pressure, medium pressure and low pressure cleaning devices, floor cleaning equipment, car washes, tank cleaning systems, steam cleaning equipment, C0 ₂ -Reingiungsgeräte or snow blasting equipment or general equipment washing systems or even windscreen cleaning equipment, devices for cleaning of measuring devices, lighting systems or measuring sensors. Other types of devices in which the fluidic components are used are devices that require uniform distribution of fluid, such as in electroplating, adhesive dispensing equipment, fluid wetting equipment, or other equipment in industrial production or process engineering, or in the food industry. These components are also used in the sanitary sector. Typical examples of this are shower heads, whirlpool, massage jets or integrated in the faucet or as a faucet attachment eg as salad shower. Additional application areas where these nozzles are integrated in devices are mixing devices, cooling units or heaters. But also to reduce the temperature stratification, the fluidic components are suitable, such as in the cooling of components or in the air conditioning. In particular, in devices for fire fighting, the invention are suitable. Through the integration of the fluidic components in firefighting devices, such as sprinkler systems or fire extinguishing systems.

Due to the wide field of application, very different requirements also arise for the fluidic components. Depending on the requirements, different input pressures or volume flows are available to the components. The advantage of these components over conventional nozzles is that they have a relatively constant spray angle α over a large process window. Therefore, for the design and description of the nozzle essentially the spray angle α is necessary. Depending on the application, fluidic components with a spray angle of 5 ° to 160 ° are required. To generate this desired angle, the inner geometry parameters must be be adjusted accordingly. Therefore, in this document, the geometric quantities are expressed as a function of the desired spray angle α.

The object is achieved by a fluidic component having the features of claim 1.

The fluidic component is used to generate a free jet, wherein the component has a flow chamber through which a fluid flow enters through an inlet opening into the flow chamber and exits the flow chamber through an outlet opening and whose flow direction is substantially parallel to the main extension direction of the flow chamber and wherein within the flow chamber, a main flow channel and bypass channels are arranged. Such fluidic components are basically known from the prior art.

In the fluidic component claimed here, the cross-sectional profile of the main flow channel in the direction of the main extension direction of the flow chamber over the entire length of the main flow channel is divergent or partially divergent and partially convergent. The object is achieved by a fluidic component having the features of claim 15.

Here, the basically known fluidic component additionally has an outlet region, in particular a channel or a region, downstream of the outlet opening, which is obstruction-free.

Advantageous embodiments are subject of the dependent claims.

Exemplary embodiments will be explained with reference to the figures. FIG. 1 schematically shows a fluidic component 1 according to an embodiment of the invention. Figures 2 and 3 show a sectional view of this fluidic component 1 along the lines A'-A "and B'-B". The fluidic component 1 comprises a flow chamber 10, which can be flowed through by a fluid flow 2. The flow chamber 10 is also known as the interaction chamber.

The flow chamber 10 comprises an inlet opening 101 with an inlet width biN, via which the fluid stream 2 enters the flow chamber 10, and an outlet opening 102 with an outlet width b _E x, via which the fluid stream 2 exits the flow chamber 10. The outlet width b _E x is greater than the inlet width b _{! N.}

The inlet opening 101 and the outlet opening 102 are arranged on two fluidically opposite sides of the fluidic component 1. The fluid flow 2 moves in the flow chamber 10 substantially along a longitudinal axis A of the fluidic component 1 (which connects the inlet opening 101 and the outlet opening 102) from the inlet opening 101 to the outlet opening 102. The longitudinal axis A in this embodiment forms an axis of symmetry of the fluidic component 1. The longitudinal axis A lies in two mutually perpendicular planes of symmetry S1 and S2, with respect to which the fluidic component 1 is mirror-symmetrical. Alternatively, the fluidic component 1 can not be constructed symmetrically (mirror).

For a specific change of direction of the fluid flow, the flow chamber 10 comprises, in addition to a main flow channel 103, two bypass ducts 104a, 104b, the main flow duct 103 (viewed transversely to the longitudinal axis A) being arranged between the two bypass ducts 104a, 104b. Immediately behind the inlet opening 101, the flow chamber 10 divides into the main flow channel 103 and the two bypass channels 104a, 104b, which are then brought together again immediately in front of the outlet opening 102.

The two bypass channels 104a, 104b are arranged symmetrically with respect to the axis of symmetry S2 (FIG. 3). According to an alternative, not shown, the bypass ducts are not arranged symmetrically. These secondary flow channels can also be positioned outside the illustrated flow plane. These channels may, for example, be realized by means of hoses outside the plane formed by S1 or through channels which are at an angle to the flow plane.

The main flow channel 103 connects the inlet opening 101 and the outlet opening 102 substantially in a straight line with one another so that the fluid flow 2 essentially flows along the longitudinal axis A of the fluidic component 1. The bypass ducts 104a, 104b extend, starting from the inlet opening 101, in a first section, each initially at an angle of substantially 90 ° to the longitudinal axis A in opposite directions. Subsequently, the bypass ducts 104a, 104b bend so that they extend in each case substantially parallel to the longitudinal axis A (in the direction of the outlet opening 102) (second section). In order to recombine the bypass ducts 104a, 104b and the main flow duct 103, the bypass ducts 104a, 104b again change direction at the end of the second section, so that they are respectively directed substantially in the direction of the longitudinal axis A (third section). In the embodiment of Figure 1, the direction of the bypass ducts 104a, 104b changes at the transition from the second to the third section by an angle of about 120 °. However, for the change of direction between these Both sections of the bypass ducts 104a, 104b are selected other than the angle mentioned here.

The bypass ducts 104a, 104b are a means for influencing the direction of the fluid flow 2, which flows through the flow chamber 10. For this purpose, the bypass ducts 104a, 104b respectively have an inlet 104a1, 104b1, which is formed by the end of the bypass ducts 104a, 104b facing the outlet opening 102, and in each case an outlet 104a3, 104b3 which extends through the end of the bypass ducts 104a facing the inlet opening 101 , 104b is formed. Through the inputs 104a1, 104b 1 flows a small part of the fluid flow 2, the secondary streams 23a, 23b (Figure 4), in the bypass channels 104a, 104b. The remaining part of the fluid flow 2 (the so-called main flow 24) exits the fluidic component 1 via the outlet opening 102 (FIG. 4). The secondary streams 23a, 23b emerge at the exits 104a3, 104b3 from the bypass ducts 104a, 104b, where they can exert a lateral (transversely to the longitudinal axis A) impulse on the fluid flow 2 entering through the inlet opening 101. In this case, the direction of the fluid flow 2 is influenced in such a way that the main flow 24 emerging at the outlet opening 102 spatially oscillates, in a plane in which the main flow passage 103 and the bypass flow passages 104a, 104b are arranged. The plane in which the main current 24 oscillates corresponds to the plane of symmetry S1 or is parallel to the plane of symmetry S1. FIG. 4, which represents the oscillating fluid flow 2, will be explained in more detail later.

The bypass ducts 104a, 104b each have a cross-sectional area which is almost constant over the entire length (from the inlet 104a1, 104b1 to the outlet 104a2, 104b2) of the bypass ducts 104a, 104b. On the other hand, the size of the cross-sectional area of the main flow passage 103 in the flow direction of the main flow 23 (that is, in the direction from the inlet port 101 to the outlet port 102) increases substantially steadily, and the shape of the main flow passage 103 is mirror-symmetrical to the planes of symmetry S1 and S2.

The main flow channel 103 can taper downstream between the inner blocks 11 a, 11 b. But to achieve an oscillation angle α of greater than 60 ° and in particular of over 80 ° but a monotonously divergent shape between the inner blocks 11 a and 11 b of the main flow channel 103 is advantageous. Alternatively or additionally, it is advantageous that no internals are located in the vicinity of the outlet 102, in order thus to achieve a high beam quality. Solutions are known in the art in which bluff bodies are positioned near the outlet to increase the spray angle at which it is burst. These installations have the disadvantage that the beam quality of the oscillating free-steel 15 (see FIG. The main flow channel 103 is separated from each bypass channel 104a, 104b by a block 11 a and by the block 11 b. The two blocks 11 a, 11 b are arranged symmetrically with respect to the mirror plane S2 in the embodiment. In principle, however, they can also be designed differently and not aligned symmetrically. In non-symmetrical alignment and the shape of the main flow channel 103 is not symmetrical to the mirror plane S2. The shape of the blocks 11 a, 11 b, which is shown in Figure 1, is only an example and can be varied. The blocks 11 a, 11 b of Figure 1 have rounded edges. There are also scharkantige edges possible. The blocks 11 a, 11 b are in this embodiment, however, designed so that a triangular or wedge-shaped flow chamber 103 is formed thereby. The shape of the flow chamber is mainly formed by the inwardly facing surfaces of the blocks 11 a, 11 b and is designated here by the number 110. The included angle is referred to herein as γ. For this purpose, the surface 110, which is formed by the line shown in FIG. 1 and the component depth t, can have a slight curvature or be formed by one or more radii, a polynomial or or and one or more straight lines or by a mixed form. To achieve a large spray angle α of more than 60 °, in particular over 80 °, it is advantageous if care is taken in the mold that the width bi os of the main flow channel 103 between the inner blocks 11 a, 11 b becomes monotonically greater downstream. If no large spray angle α is desired, a locally non-propagating shape of the main flow channel 103 is advantageous.

At the entrance 104a1, 104b1 of the bypass ducts 104a, 104b, also separators 105a, 105b are provided in the form of indentations. In this case, at the entrance 104a 1, 104b 1 of each bypass duct 104a, 104b each project a recess 105a, 105b over a portion of the peripheral edge of the bypass duct 104a, 104b in the respective bypass duct 104a, 104b and changed at this point while reducing the cross-sectional area of its cross-sectional shape. In the embodiment of Figure 1, the portion of the peripheral edge is chosen so that each indentation 105a, 105b (among other things) is directed towards the inlet opening 101 (oriented substantially parallel to the longitudinal axis A). Alternatively, the separators 105a, 105b may be oriented differently. The separation of the secondary streams 23a, 23b from the main stream 24 is influenced and controlled by the separators 105a, 105b. By the shape, size and orientation of the separators 105a, 105b, the amount flowing from the fluid stream 2 into the bypass channels 104a, 104b and the direction of the secondary streams 23a, 23b can be influenced. This in turn leads to an influencing of the outlet angle of the main flow 24 at the outlet opening 102 of the fluidic component 1 (and thus to an influence on the oscillation angle a), with which the main flow 24 at the Outlet opening 102 oscillates. By selecting the size, orientation and / or shape of the separators 105a, 105b, the profile of the main flow 24 exiting at the outlet opening 102 can thus be influenced in a targeted manner. Alternatively, it is also possible to provide a separator only at the inlet of one of the two bypass ducts. Particularly advantageous is the position of the separators 105a, 105b above the maximum width bn amax, bu bmax-

The inlet opening 101 of the flow chamber 10 is upstream of a funnel-shaped projection 106, which tapers in the direction of the inlet opening 101 (downstream). The flow chamber 10 tapers in the region of the outlet opening 102 downstream of the inner blocks 11 a, 11 b. The taper is formed by an exhaust passage 107 extending between the separators 105a, 105b and the exhaust port 102. For components without separators 105a, 105b, the outlet channel 107 begins at the bypass channel inlet 104a1, 104b1. The funnel-shaped projection 106 and the outlet channel 107 taper in such a way that only their width, that is to say their extent in the plane of symmetry S1 perpendicular to the longitudinal axis A, decreases in each case downstream. The taper does not affect the depth, that is, the extent in the plane of symmetry S2 perpendicular to the longitudinal axis A, the neck 106 and the outlet channel 107 (Figure 2). Alternatively, the lug 106 and the outlet channel 107 may also taper in width and depth, respectively. Further, only the lug 106 may taper in depth or width while the outlet channel 107 tapers both in width and depth, and vice versa. The extent of the taper of the outlet channel 107 influences the directional characteristic of the fluid flow 2 emerging from the outlet opening 102 and thus its oscillation angle a. The shape of the funnel-shaped projection 106 and the outlet channel 107 are shown in FIG. 1 by way of example only. Here, their width decreases downstream each linear. Other forms of rejuvenation are possible. The length of the funnel-shaped projection h oe in this embodiment corresponds at least to the inlet width bin, so h oe> bi.

The inlet opening 101 and the outlet opening 102 each have a rectangular cross-sectional area. These each have the same depth (extension in the plane of symmetry S2 perpendicular to the longitudinal axis A, Figure 2), but differ in their width b, bex (expansion in the plane of symmetry S1 perpendicular to the longitudinal axis A, Figure 1). In particular, the outlet opening 102 is wider than the inlet opening 101. The outlet width b _E x is greater than the narrowest cross-sectional constriction upstream of the flow chamber. The narrowest cross-sectional constriction can be either the minimum width of the flow chamber or the intake width bn b _iN. Typically, both length dimensions range between 0.01 mm and 250 mm. These geometric dimensions depend on the required volume flow or on the boundary condition, how much Fluid should flow through the component. Therefore, no further limiting measures can be given here. However, the dimensions mentioned may differ from the specified dimensions. Typically, the difference between the width b and bn is max. 40%. That is, the width bn may be up to 40% larger or smaller than the width b _iN . Preferably, the combination that the width bn is less than or equal to the width biN.

Two variants are advantageous for connecting the exit region 108 to the functional geometry.

First, with a radius 109 that is smaller than the minimum width of bi or bn. An extreme value, which results in a sharp-edged outlet 102, is a radius of zero.

Due to the higher mechanical stability, a radius 109 is to be preferred. After the radius follows a nearly straight-line section. This nearly or rectilinear section, which may also be formed by a polynomial, is at an angle δ to one another.

This angle δ can have different dimensions. Advantageously, an angle δ derived from the desired oscillation angle a. A deviation of + 12 ° and - 40 ° possible from the oscillation angle is possible, ie α - 40 ° <δ <α + 12 °. A particularly preferred deviation is + 7 ° and - 30 °, so α - 30 ° <δ <α + 7. Thus, in the case when the free-running oscillation angle α is too large, by a smaller angle δ of the oscillation angle α on the Angle δ can be reduced.

But the angle δ can also be used to increase the spray angle α, in the case when the freely dwindling oscillation angle α is insufficient. Then the spray angle can be increased up to 12 ° if the angle δ is dimensioned by a maximum of 12 ° greater than the oscillation angle a. In particular, an enlargement of the angle δ of at most 4 ° from the free-running emerging free jet 15 is preferred.

For some applications, in particular in which a more uniform distribution is desired, it is advantageous if the almost straight-line sections after the radius 109 do not touch the oscillating free jet 15, as shown by way of example in FIG. 4 c). Then the angle δ should be chosen to be considerably larger than the oscillation angle α, for example 180 °. The length of the exit region os positively influences the beam quality of the oscillating fluid jet. The longer the length of the exit region is os, the stronger the outgoing fluid jet is bundled. For a desired increased fluid jet quality, a length os of at least half of the radius 109 is necessary. It is particularly preferred if h os corresponds at least to the outlet width bx. The maximum length h os corresponds to the component length I.

FIG. 4 shows three snapshots of a fluid flow 2 for illustrating the flow direction (flow lines) of the fluid flow 2 in a fluidic component 1 during an oscillation cycle (FIGS. A) to c)). The fluidic component 1 from FIG. 4 differs from the fluidic component 1 from FIGS. 1 to 3 in particular in that no separators 105 are provided. The component length I of the fluidic component 1 from FIG. 4 is 22 mm and the component width b = 20 mm. The width b of the inlet opening 101 is 3.2 mm and the width bu is 2.8 mm. The outlet width bex is 5 mm. The component depth t is constant in this embodiment and is 2 mm. The main flow channel 103 has a maximum width bi osmax, which are located between the blocks 11 a, 11 b, of 13.07 mm. This maximum width b ₀ 3max is defined at the position of the radius to the straight line from the inner block surface 110 merges here in this embodiment. The fluid flowing through the fluidic component 1 has at the inlet opening 101 a pressure of 0.11 bar and a volume flow of 1.5 l / min, the fluid being water with a temperature of 20.degree. However, the illustrated fluidic component 1 is basically also suitable for gaseous fluids. In Figures a) and c), the flow lines for two deflections of the exiting main flow 24 are shown, which correspond approximately to the maximum deflections. The angle which the exiting main flow 24 passes between these two maxima is the oscillation angle a. Figure b) shows the flow lines for a position of the exiting main flow 24, which lies approximately in the middle between the two maxima from the figures a) and c). The following describes the flows within the fluidic component 1 during an oscillation cycle.

By introducing a single accidental or targeted disturbance, the fluid flow 2 is laterally deflected in the direction of the main flow channel 103 facing side wall 110a of a block 11 a, so that the direction of the fluid flow 2 increasingly deviates from the longitudinal axis A until the fluid flow is deflected maximum. By the so-called Coanda effect, the largest part of the fluid flow 2, the so-called main flow 24, attaches itself to the side wall of the one block 11b and then flows along this side wall 110b. In this case, the angle γ in conjunction with the Angle ß later the oscillation angle a. Depending on the boundary conditions or the field of application of the fluidic component 1, the angle γ changes. The inner side 110 of the main flow channel 103 and the inside of the outlet channel 107 are at an angle ε to each other. The angle ε is approximately 90 ° in the illustrated embodiment. In other embodiments, the angle ε may be in the range between 80 ° and 110 ⁰ . As a result, the angles γ and the angle β are also directly related, if they are fluidic components with a large spray angle of at least 60 °. Due to the non-linear behavior of the flow, a detailed specification is not practicable here.

In the area between the main flow 24 and the other block 11 a, a recirculation area 25a is formed. In this case, the recirculation area 25a increases the more the main flow 24 to the side wall of a block 11 b applies. The main stream 24 exits the outlet port 102 at a time varying angle with respect to the longitudinal axis A. In Figure 4c), the main flow 24 is applied to the side wall of the one block 11 a and the recirculation area 25b has its maximum size. In addition, the main flow 24 emerges from the outlet opening 102 with approximately the greatest possible deflection. A small part of the fluid flow 2, the so-called sidestream 23a, 23b, separates from the main flow 24 and flows into the bypass ducts 104a, 104b via their inlets 104a1, 104b1. In the situation shown in Figure 4c) (due to the deflection of the fluid flow 2 in the direction of the block 11 a) of the part of the fluid flow 2, which flows into the bypass duct 104 b, which borders on the block 11 b, on whose side wall, the main flow 103 does not apply, significantly larger than the part of the fluid flow 2, which flows into the bypass duct 104 a, which adjoins the block 11 a, on the side wall of which the main current 103 applies. In FIG. 4c), therefore, the secondary flow 23b is significantly greater than the secondary flow 23a, which is almost negligible. As a rule, the deflection of the fluid flow 2 into the bypass ducts 104a, 104b can be influenced and controlled by separators. The secondary streams 23a, 23b (in particular the secondary stream 23b) flow through the secondary flow channels 104a or 104b to their respective outlets 104a2, 104b2 and thus give a pulse to the fluid stream 2 entering at the inlet opening 101. Since the sub-stream 23b is larger than the sub-stream 23a, the pulse component resulting from the sub-stream 23b outweighs.

The main stream 24 is thus pressed by the pulse (the secondary stream 23 b) to the side wall of the block 11 a. At the same time, the recirculation area 25b moves toward the entrance 104b1 of the bypass passage 104b, thereby disturbing the supply of fluid into the bypass passage 104b. The momentum component of the Side stream 23b results, it decreases. At the same time, the recirculation area 25b decreases, while a further (growing) recirculation area 25a is formed between the main flow 24 and the side wall of the block 11a. In this case, the supply of fluid in the bypass duct 104a increases. The pulse component resulting from the bypass 23a increases with it. The pulse components of the secondary streams 23a, 23b continue to approach in the further course, until they are the same size and cancel each other out. In this situation, the incoming fluid stream 2 is not deflected (Figure a)), so that the main flow 24 approximately centrally between the two blocks 11 a, 11 b moves and exits without deflection from the outlet opening 102.

Further, the supply of fluid into the bypass passage 104a continues to increase, so that the pulse component resulting from the bypass 23a exceeds the pulse component resulting from the bypass 23b. The main flow 24 is thereby pushed further and further away from the side wall of the block 11 a until it abuts the side wall of the opposite block 11 b due to the Coanda effect (Figure 4c)). The recirculation area 25b dissolves while the recirculation area 25a increases to its maximum size. The main flow 24 now emerges from the outlet opening 102 with maximum deflection, which has an inverse sign compared to the situation of FIG. 4 b).

Subsequently, the recirculation area 25a will migrate and block the entrance 104a1 of the bypass duct 104a, so that the supply of fluid here again decreases. As a result, the secondary flow 23b will deliver the dominant momentum component so that the main flow 24 is again forced away from the side wall of the block 11b. The changes described are now in reverse order.

By the operation described, the main flow 24 exiting at the outlet port 102 oscillates about the longitudinal axis A in a plane in which the main flow passage 103 and the bypass passages 104a, 104b are arranged, so that a fluid jet drifting back and forth is generated. In order to achieve the described effect, a symmetrical structure of the fluidic component 1 is not absolutely necessary.

FIG. 5 shows a fluidic component 1 without a flow separator 105. In addition, here is the narrowest cross section between the inner blocks 11 a, 11 b at the width b _n . In addition, this component has no radius 109 or an infinitesimally small radius at the outlet 102. This component shows, by way of example, important relationships of the geometric features which are required for generating large spray angles α of more than 60 °, in particular more than 80 °. The angle β is equal to or greater than the desired oscillation angle α to choose. It is preferred if the angle ß is greater than the desired oscillation angle et. The angle β can be up to 70% greater than the oscillation angle a to be achieved.

The length of the flow chamber h ₀ 3 is equal to or preferably greater than the maximum width of the flow chamber bi ₀ 3max, in particular for fluidic components with over 0.005 bar inlet pressure. To increase the beam quality, an increase in the length h os (see FIG. In the case of such fluidic components which have an inlet pressure of more than 0.05 bar at the inlet, the length h os should be at least bi 4. Particularly preferred is a length h os of at least bex.

The geometric dimension bi o7 located between the outlet 102 and the inner block 11 is greater than or equal to the smaller dimension of bi or bn. The length of bi o7 can be up to 100% greater than the smaller measure of biN or bn. This measure is dependent on the desired oscillation angle α. The larger the oscillation angle α should be, the larger the width bi ₀ 7. Also, the outlet width bex depends on the desired oscillation angle a. In the embodiment illustrated here, the outlet width b _E x is determined by the following law: bex = min (bn, biN) / [sin (90 ° -α / 2)] ± 30%. For fluidic components with a flow separator 105, a higher deviation of 45% is possible. Due to the non-linear nature of the flow, no more specific indication is possible here, but to be determined by those skilled in the art with the known flow design tools.

The width bi ₀ corresponds to 3max of the flow-relevant relevant measure bi o3oben on this component. The dimension bi ₀ 3oben is located in the upper third, ie in the last downstream located third of the main flow channel 103. This width bi o3oben is measured at the position at which the main flow channel 103 with straight walls laterally to the side flow channels 104 a, 104 b merges into a curvature namely at the inflection point of the curved surface. This turning point can also be called a bow change. At this point, the direction of the tangent changes from one point to the next point. In FIG. 5, these points also mark the maximum longitudinal extension of the main flow channel 103 in the flow chamber 10 in the direction of the outlet opening 102. For the measure 3oben bi ₀ following relationship bex <bi 03 Top <3 ^* BTX This is, for example, small radii, so the radius mm smaller than'm 2, for example less than 3.5 the case.

The fluidic component 1 shown in Figure 6 corresponds to that of Figure 1 with the difference that the inner surfaces 110 are formed differently by the blocks 11 and the outlet region 108 is significantly longer pronounced. Such components with and without exit region 108 are particularly advantageous for cleaning applications or for fluid distribution applications. In the fluidic component 1 shown here, the main flow chamber 103 between the inner blocks 11 a, 11 b has a bulbous shape. Upstream of the flow chamber 103 in the first part is monotonically larger and in the rear part, the flow chamber 103 narrows again. The resulting minimum width bi ₀ 3min of the flow chamber 103 should have the following size: b _n <bi 03min <3 ^* bex. Again, the width bi o3min the aerodynamically relevant width b ₃ corresponds ooben. The upper width bi osyn is determined at the inflection point of the inwardly directed shape of the inner blocks 11 a, 11 b. As with the other embodiments, the following relationship applies here bfiX <bl 03oben <3 "bfiX.

In these components, the oscillation mechanism deviates from the oscillation mechanism described in FIG. The difference is that the fluid from the inner block 11b first flows into the bypass duct inlet 104a1 instead of into the bypass duct inlet 104b1.

The fluidic component 1 in FIG. 7 differs from the other components in that the flow chamber 103 has an almost constant flow chamber width bio3 in the upper two-thirds, ie downstream in the last two-thirds range. Therefore, the fluidically relevant width bi ₀ 3oben determined at the position at which the flow chamber 103 facing inner surfaces 110 a and 110 b of the blocks 11 a, 11 b undergoes a change in direction in the direction of the Nebenstromkanaleinlässe 104 a 1, 104 b 1, ie the inflection point. In other words, the position for ascertaining the flow-related relevant width is determined at the point at which the curvature of the surfaces 110a, 110b changes abruptly so that at this position the main flow 24 no longer follows the surface. This is the case, for example, with a change in curvature of at least 3 ° along a 0.5 mm pitch. In this fluidic component, the spray angle α is largely determined by the angle β.

To connect the divergent portion of the flow geometry, the two known from Figure 1 two variants are advantageous. For achieving a good Spraying characteristic is a maximum length of the divergent portion os of os <I. Particularly preferred is a length os of b _E x <hos <1/3.

A further embodiment of the fluidic component with an exit region 108 is shown in FIG. The embodiment variant of the fluidic component 1 in FIG. 8 differs from the fluidic component of FIG. 6 in that the bulbous structure is not in the upper third, that is to say downstream, of the flow chamber 103, but in the lower third of the flow chamber 103. The drop-shaped flow chamber 103 causes a very homogeneous flow distribution. The drop shape is formed by a very large divergent enlargement of the flow chamber 103 downstream of the minimum width of the flow chamber bn, in the lower half of the flow chamber followed by a constriction of the flow chamber. Particularly advantageous is an almost rectilinear or piecewise straight surface 110a, 110b. These surfaces 110a, 110b include the angle γ.

In contrast to the other components mentioned, the oscillation angle α is determined directly via the angle γ. Therefore, for the angle γ, the following relationship α - 10 ° <γ <α + 10 °. In contrast to the other components, in this component the main flow 24 does not flow via the outlet channel 107 but directly out of the outlet bex. Therefore, the angle β here has no great influence on the oscillation angle a. As with the other components, the outlet width bi o3min is greater than bsx. Here, the outlet width bi 03min corresponds to the uppermost width bi 03 upper. It is particularly preferred that the outlet width bpx be greater than the width bi 03min added with half the inlet width biN, ie bex> bi 03min + biN 2.

Claims

claims

1 . Fluidic component (1) for generating a free jet (15), wherein the component (1) has a flow chamber (10) through which a fluid flow (2) can pass, which enters the flow chamber (10) through an inlet opening (101) and exits the flow chamber (10) through an outlet opening (102) and whose flow direction is substantially parallel to the main extension direction of the flow chamber (10) and wherein a main flow channel (103) and branch flow channels (104) are arranged within the flow chamber (10), characterized in that the cross-sectional profile of the main flow channel (103) in the direction of the main extension direction of the flow chamber (10) over the entire length of the main flow channel (103) is divergent or partially divergent and partially convergent.

2. Fluidic component according to claim 1, characterized in that the divergent portion of the cross-sectional profile of the flow chamber (10) is monotonous, in particular linear monotonous.

3. Fluidic component according to claim 1 or 2, characterized in that the cross-sectional profile of the flow chamber (10) is formed kink-free.

4. Fluidic component according to at least one of the preceding claims, characterized in that the flow chamber (10) has a fluidically relevant

Width bi ₀ 3oben, which is greater than an outlet width bex the outlet opening (102), but in particular is smaller than 3-btx, wherein the width bi ₀ 3oben at the position at which the main flow channel (103) with straight walls laterally to the bypass ducts (104a, 104b) merges into a curvature and that at the inflection point of the curvature.

5. Fluidic component according to at least one of the preceding claims, characterized in that for generating the free jet (15) with an oscillation angle α of greater than 60 ° and in particular of over 80 °, the walls of the flow chamber (10) are arranged so that Cross-sectional profile of the flow chamber (10) along the main extension direction of the flow chamber (10), in particular between the inner blocks (11 a, 11 b), a monotonously divergent shape, so that the flow chamber has a triangular or wedge-shaped flow chamber (10), in particular the width (bi _ra ) of the main flow _channel (103) between the inner blocks (11 a, 11 b) monotonously increases downstream.

6. Fluidic component according to at least one of the preceding claims, characterized in that an inner side (110) of the main flow channel (103) and the inside of an outlet opening (102) leading outlet channel (107) are at the angle (ε) to each other, wherein the angle is between 80 ° and 110 °, in particular at 90 °.

7. Fluidic component according to at least one of the preceding claims, characterized in that the inner sides of an outlet channel (102) leading outlet channel (107) are at an angle (ß), which is equal to or greater than the selected oscillation angle (Q), in particular, it is larger than the oscillation angle (a).

8. Fluidic component according to at least one of the preceding claims, characterized in that the length (h os) of the main flow channel (103) is equal to or greater than the maximum width (bi ₀ 3max) of the main flow channel (103).

9. Fluidic component according to at least one of the preceding claims, characterized in that the distance bw) across the flow direction between the outlet (102) and the outlet of the inner block (11) is equal to or greater than the smaller dimension of b or bu, in particular, the distance (bi ₀ 7) can be up to 100% greater than the smaller measure of biN or bu.

10. A fluidic component according to at least one of the preceding claims, characterized in that outlet width (bex) of the outlet opening (102) bsx = min (bii, bw) / [sin (90 ° - α / 2)] ± 30%, wherein in the case of the presence of a flow separator (105), a higher deviation is necessary due to the non-linear behavior of a fluid, and bex = min (bn, biN) / [sin (90 ° -α / 2)] ± 45%.

11. Fluidic component according to at least one of the preceding claims, characterized in that for the angle (γ) enclosed by the inner walls of the inner blocks (11a, 11b): α - 10 ° <γ <α + 10 °, with α as the oscillation angle.

12. Fluidic component according to at least one of the preceding claims, characterized in that for outlet width bex bex> bi o3min + bi / 2, where bi 03min is the minimum width of the main flow channel (103) and b _{iN is} the inlet width of the flow chamber (10) ,

13. Fluidic component according to at least one of the preceding claims, characterized in that the main flow channel (103) has a teardrop shape through a divergent enlargement of the flow chamber (103) downstream of the minimum width bn of the flow chamber (103) is formed in the lower half of the flow chamber (103) followed by a constriction of the flow chamber (103).

14. A fluidic component according to claim 13, characterized in that for the of the straight parts of the inner walls of the inner blocks (11 a, 11 b) formed angle (γ) applies: α - 10 ° <γ <α + 10 °, with α as the oscillation angle.

15. Fluidic component for generating a free jet (15), wherein the component (1) has a flow chamber (10) through which a fluid flow (2) can flow, which enters the flow chamber (10) through an inlet opening (101) and through an outlet opening (102) from the flow chamber (10) and its flow direction is substantially parallel to the main extension direction of the flow chamber (10), wherein within the flow chamber (10) a main flow channel (103) and bypass channels (104) are arranged, characterized in that an exit region (108), in particular a channel or a region, downstream of the outlet opening (102) is obstruction-free.

16. A fluidic component according to claim 15, characterized in that the outlet region (108) in the flow direction laterally bounded by walls which are arranged at an angle (δ), wherein the size of the angle (δ) from the predetermined oscillation angle (a) depends : α - 40 ° <δ <α + 12 °, in particular α - 30 ° <δ <α + 7 °.

17. Fluidic component according to claims 15 or 16, characterized in that the angle (δ) is greater than the oscillation angle a, in particular 180 °.

18. The fluid component according to claim 15, characterized in that the length (h os) of the outlet region (108) in the flow direction is at least half of the radius of curvature (109) at the outlet of the flow chamber (10) and at the entrance to the outlet region (108) corresponds or the length (h os) of the outlet region (108) in the flow direction corresponds at least to the outlet width (bex) of the flow chamber (10).

19. Fluidic component according to claim 15, characterized in that the length (h os) of the outlet region (108) in the flow direction is at least b _iN / 4, in particular of at least b _E x.

20. Fluidic component according to claim 15, characterized in that for the maximum length (h os) of the exit region (108) in the flow direction os <I, in particular b _E x <h os <I / 3.

21. Fluidic component according to at least one of claims 1 5 to 20, characterized in that the outlet width (bex) of the flow chamber (10) is greater than the inlet width (biN) of the flow chamber (10), in particular the outlet width (bsx) is greater than that narrowest cross-sectional constriction upstream of the flow chamber (10), wherein narrowest cross-sectional constriction be the minimum width (bn) of the flow chamber (10) or the inlet width (birg).

22. Fluidic component according to at least one of claims 1 to 14 and at least one of claims 15 to 21.

23. A fluidic component according to at least one of the preceding claims, characterized in that the length (h oe) of a funnel-shaped projection of the inlet opening (101) is upstream in the flow direction, at least as large as the inlet width b ^: h oe> bin.

24. Fluidic component according to at least one of the preceding claims, characterized in that the minimum width (bn) of the main flow channel (103) or the flow chamber (10) is less than or equal to the width (bi) of the inlet.

25. Fluidic component according to at least one of the preceding claims, characterized by separators (105a, 105b) at the entrance (104a1, 104b1) of

Nebenstromkanäle (104a, 104b), in particular in the form of indentations, wherein the separators (105a, 105b) above the maximum width bi 1 amax, bu bmax are arranged, wherein the maximum width bu amax, bu bmax the maximum width between the inner blocks 11 is.

26. Fluidic component according to at least one of the preceding claims, characterized in that the radius of curvature (109) at the outlet of the flow chamber (10) and at the entrance to the outlet region (108) is smaller than the minimum width bi or bn.

27. Fluidic component according to at least one of the preceding claims, characterized in that the length of the flow chamber (cs) is equal, but in particular greater than the maximum width of the flow chamber (bi ₀ 3max).

28. Fluidic component according to at least one of the preceding claims, characterized in that in the case of essentially vase-shaped flow channels (103): 29. Device with at least one of the fluidic components according to claim 1, in particular a spray device for water, fertilizer or pesticide, a cleaning device for crockery, goods or parts, a pressure cleaning device, a car wash, a cleaning device for sensors, disks or surfaces, a fluid distribution device, a sanitary appliance, a firefighting device, in particular a sprinkler system or a fire extinguishing system.