EP3434998A1 - Ventilation device - Google Patents

Abstract

Ventilation device (10) for installation in a room (1), the ventilation device (10) having, in the installed state, a flat ventilation element (100) facing in the spatial direction and having air passage openings, and with an outflow box (20) on a rear side (101) opposite the spatial direction the ventilation element (100) is provided with an air supply (21, 22; 23, 24, 25) for supplying an air flow and the ventilation element (100) has a plurality of slots arranged in a grid comprising rows (109) and columns (110). (102) as air passage openings and the slits (102) each have a slit length (L) between 2 and 10 mm and a slit width (W) between 0.1 and 0.8 mm, the line grid (Z1) being 1 mm to 15 mm and the column grid (S1) is 0.5 x L to 2 x L, the ventilation element (100) comprising at least one active surface area (O A ) and at least one inactive surface area (O I ) and for at least one characteristic Ab measurement x A of the active surface area (O A ) applies: 3 L ‰¤ x A ‰¤ 50 L .

Description

The invention relates to a ventilation device according to claim 1, a ventilation device with such ventilation devices according to claim 23, and a method for operating such a ventilation device according to claim 24.

definitions

Induction is understood to mean the proportion of room air which is entrained or entrained by the primary air flow supplied by means of the ventilation device. In this case, an induction number of 10 means that, for example, 1 m ³ primary air flow by a factor of 10 more, ie 10 m ³ room air moves. A better mixing of the room air is achieved if the induction number of the ventilation device is as large as possible. On the other hand, standards (eg the Swiss SIA standard 382/1, corresponding to EN 13779) should be adhered to in order, for example, to guarantee the freedom of movement of such a ventilation device.

The permissible room air velocity according to SIA standard 382/1 at 50% humidity, depending on the room temperature, is between approx. 120 m / s at 20 ° C and approx. 170 m / s at 26 ° C.

The term "surface load" is understood to mean the volume flow of the supply air per time and the active surface area through which it flows in m ³ / (hm ² ).

Under an active area is a continuous with a slot pattern as described in more detail below, in particular Slot grid provided and thus air-permeable surface of a ventilation element understood.

Inactive areas are air-impermeable areas of a ventilation element in which the slot pattern is either covered, closed or missing.

The term "throw distance" is understood here to mean the usual term in air conditioning technology, namely the distance from the outlet opening, at which the supply air or there already mostly mixed air flow is braked to a speed of 0.25 m / s.

Background of the Invention, Prior Art

In physical relationships, which play a role in the design of a ventilation solution with ventilation holes, there are complex interactions. That's why the task is to offer appropriate solutions that are efficient and still cost-effective. In addition, it is important to provide the largest possible cooling capacity per room volume without at the same time causing disturbing draft phenomena.

• Die Stärke und Richtung des Luftstroms, der in einen rückwärtigen Abströmkasten geführt wird, hat einen Einfluss auf die Stärke der einzelnen feinen Primärluftströmungen, die durch Luftdurchtrittsöffnungen eines Lüftungselements austreten.
• Es scheint besser zu sein, wenn dieser Luftstrom nach dem Eintritt in den Abströmkasten erst eine Umlenkung oder Ablenkung erfährt, um möglichst entlang der Rückseite des Lüftungselements zu "fliessen", bevor der Durchtritt durch die Luftdurchtrittsöffnungen in Richtung des Raumes erfolgt.
• Beim Durchtritt durch die Luftdurchtrittsöffnungen in Richtung des Raumes wird durch Induktion von dem Primärluftstrom an jedem der Luftdurchtrittsöffnungen ein Sekundärluftstrom induziert. Hier hat sich gezeigt, dass es einen Zusammenhang gibt zwischen der gesamten Kantenlänge (Umfang) einer Luftdurchtrittsöffnung, der Fläche dieser Luftdurchtrittsöffnung und der Induktionswirkung. Es wurde ermittelt, dass eine kreisförmige Luftdurchtrittsöffnung ein ungünstigeres Verhältniss von Umfang zur Fläche aufweist als ein Schlitz.
• Ausserdem wurde festgestellt, dass es eine Rolle spielt, wie gross der sogenannte freie Querschnitt pro Flächeneinheit des Lüftungselements ist. Wenn der freie Querschnitt pro Flächeneinheit zu gross ist, dann tritt der Luftstrom aus dem Abströmkasten nahezu ungehindert und mit niedriger Strömungsgeschwindigkeit durch die Luftdurchtrittsöffnungen hindurch. Bei einem zu kleinen freien Querschnitt pro Flächeneinheit tritt eine unerwünschte Stauwirkung im Abströmkasten ein. Optimal ist ein freier Querschnitt, der im Bereich zwischen 3 und 20% liegt.
• Eine bessere Durchmischung der Raumluft wird erzielt, wenn die Induktionszahl der Lüftungsvorrichtung möglichst gross ist. Auf der anderen Seite sollten Normen (z.B. die Schweizer SIA Norm 382/1) eingehalten werden, was z.B. die Zugfreiheit einer solchen Lüftungsvorrichtung anbelangt.
• Weiterhin spielt die Leistung der Lüftungsvorrichtung eine grosse Rolle, da die Leistung im Prinzip einen direkten Zusammenhang zur Wirtschaftlichkeit und zu den Kosten einer Lüftungsvorrichtung hat.

The invention is based on the findings of CH 702 748 Therefore, their description and drawings are therefore an integral part of the present invention and their most important findings are set out again below. Thus, the following Swiss patent has already been recognized:

• The strength and direction of the air flow, which is guided into a rear outflow box, has an influence on the strength of the individual fine primary air flows, which emerge through air passage openings of a ventilation element.
• It seems to be better, if this air flow after entering the discharge box first undergoes a deflection or deflection in order to "flow" as far as possible along the back of the ventilation element, before the passage through the air passage openings in the direction of the room.
• When passing through the air passage openings in the direction of the space, a secondary air flow is induced by induction of the primary air flow at each of the air passage openings. Here it has been shown that there is a relationship between the total edge length (circumference) of an air passage opening, the surface of this air passage opening and the induction effect. It has been found that a circular air passage has a more unfavorable ratio of perimeter to area than a slot.
• In addition, it was found that it plays a role, what is the so-called free cross-section per unit area of the ventilation element. If the free cross section per unit area is too large, then the air flow from the discharge box passes through the air passage openings almost unhindered and at low flow rate. If the free cross section per unit area is too small, an undesirable accumulation effect occurs in the outflow box. Is optimal a free cross-section ranging between 3 and 20%.
• A better mixing of the room air is achieved if the induction number of the ventilation device is as large as possible. On the other hand, standards (eg the Swiss SIA standard 382/1) should be complied with, for example concerning the freedom of draft of such a ventilation device.
• Furthermore, the performance of the ventilation device plays a major role, since the performance in principle has a direct relationship to the economy and the cost of a ventilation device.

• Fig. 1A eine schematische Schnittansicht einer ersten Ausführungsform des Standes der Technik, die einen Abströmkasten und ein flächiges Lüftungselement umfasst;
• Fig. 1B eine schematische Ausschnittsvergrösserung des Lüftungselements nach Fig. 1A mit einem Stanzschlitz;
• Fig. 2 eine schematische Schnittansicht einer zweiten Ausführungsform, die einen Abströmkasten und ein wannen- oder trogförmiges Lüftungselement umfasst;
• Fig. 3 eine schematische Schnittansicht einer dritten Ausführungsform der Erfindung, die einen Anströmkasten und einen Abströmkasten sowie ein flächiges Lüftungselement umfasst;
• Fig. 4 eine schematische Schnittansicht einer vierten Ausführungsform der Erfindung, die einen Anströmkasten und einen Abströmkasten sowie ein wannen- oder trogförmiges Lüftungselement umfasst;
• Fig. 5A eine schematische Unteransicht eines Abschnitts eines Lüftungselements;
• Fig. 5B eine schematische Ausschnittsvergrösserung des Lüftungselements nach Fig. 5A;
• Fig. 6A eine schematische Schnittansicht eines Lüftungselements des Standes der Technik;
• Fig. 6B eine schematische Unteransicht des Lüftungselements nach Fig. 6A;
• Fig. 7A eine schematische Unteransicht eines weiteren Lüftungselements mit auf "Lücke" sitzenden Stanzschlitzen;
• Fig. 7B eine schematische Unteransicht eines weiteren Lüftungselements mit auf "Lücke" sitzenden Stanzschlitzen;
• Fig. 8 eine schematische Unteransicht eines weiteren Lüftungselements mit partiell überlappenden Stanzschlitzen.

First, details and advantages of this prior art will be described by way of embodiments and in part with reference to the drawings. All figures are schematic and not to scale, and corresponding structural elements are given the same reference numerals in the different figures, even if they are designed differently in detail. Show it:

• Fig. 1A a schematic sectional view of a first embodiment of the prior art, which comprises an outflow box and a planar ventilation element;
• Fig. 1B a schematic enlarged detail of the ventilation element according to Fig. 1A with a punched slot;
• Fig. 2 a schematic sectional view of a second embodiment comprising an outflow box and a trough or trough-shaped ventilation element;
• Fig. 3 a schematic sectional view of a third embodiment of the invention, a Anströmkasten and an outflow box and a planar ventilation element comprises;
• Fig. 4 a schematic sectional view of a fourth embodiment of the invention, comprising a Anströmkasten and an outflow box and a trough or trough-shaped ventilation element;
• Fig. 5A a schematic bottom view of a portion of a ventilation element;
• Fig. 5B a schematic enlarged detail of the ventilation element according to Fig. 5A ;
• Fig. 6A a schematic sectional view of a ventilation element of the prior art;
• Fig. 6B a schematic bottom view of the ventilation element according to Fig. 6A ;
• Fig. 7A a schematic bottom view of another ventilation element with sitting on "gap" punching slots;
• Fig. 7B a schematic bottom view of another ventilation element with sitting on "gap" punching slots;
• Fig. 8 a schematic bottom view of another ventilation element with partially overlapping punching slots.

In the following, the principle shown there will be described with reference to a first embodiment, which in FIG Fig. 1A and Fig. 1B is shown.

It is about ventilation devices 10, which are designed for installation in a room 1. These ventilation devices 10 may be designed for ventilation, air conditioning and / or heating. Preferably, it is Ventilation devices 10 for air conditioning, which cause a cooling effect in the room 1 by an air flow L1 is supplied, the temperature of which is below the temperature of the room air in the room 1.

In the mounted state, the ventilation device 10 comprises a planar ventilation element 100 with air passage openings facing in the direction of the space. The planar ventilation element 100 may extend parallel to a ceiling. An outflow box 20 is arranged in this embodiment on a rear side opposite the spatial direction 101 of the ventilation element 100. Inside the Abströmkastens 20, an air supply 21, 22 is provided for supplying an air flow L1. The ventilation element 100 comprises a plurality of punching slots 102, which serve as air passage openings. Each of the punching slots 102 has a slot length L between 2 and 10 mm and a slot width W between 0.1 and 0.8 mm, such as in FIG Fig. 5B shown. The ratio between slot length L and slot width W is therefore between 2.5 and 100 in all embodiments. In addition, the rear side 101 of the ventilation element 100 has a regular arrangement of depressions 106 (see, for example, FIGS Fig. 6B ) formed opposite a rear (main) plane E of the ventilation member 100 in the space direction. That is, these depressions are lower on the back side 101 than the level of the rear (main) plane E.

• Bereiche in denen sich Stanzschlitze 102, 102' befinden (in den Figuren 7A und 7B als schwarze Flächen gezeigt),
• Vertiefung 106 (in den Figuren 7A und 7B als weisse Flächen gezeigt), die vorzugsweise die Stanzschlitze 102, 102' umgeben,
• Übergangsbereiche 105 (in den Figuren 7A und 7B durch gestrichelte Umrandungslinien angedeutet), die jeweils den Übergang zwischen einer Vertiefung 106 und einem in der (Haupt-)Ebene E liegenden Flächenabschnitt 107 kennzeichnen, und
• Stege 104 (auch Flächenabschnitte 107 genannt), die in der (Haupt-)Ebene E liegen. Die Flächenabschnitte 107, die quasi auf dem Normalniveau der (Haupt-)Ebene E liegen, sind in den Figuren 7A und 7B als schraffierte Fläche gezeigt.

The rear side 101 can be uniformly structured in all embodiments. Two corresponding examples are in the FIGS. 7A and 7B shown. These Examples can be applied to all embodiments. In these examples, the back 101 can be divided into principle in

• Areas in which punched slots 102, 102 'are located (in the FIGS. 7A and 7B shown as black areas),
• Well 106 (in the FIGS. 7A and 7B shown as white areas), which preferably surround the punching slots 102, 102 ',
• Transition areas 105 (in the FIGS. 7A and 7B indicated by dashed outline lines), each of which mark the transition between a depression 106 and a plane lying in the (main) plane E surface portion 107, and
• Webs 104 (also called surface portions 107) lying in the (main) plane E. The surface portions 107, which are virtually at the normal level of the (main) level E, are in the FIGS. 7A and 7B shown as hatched area.

The example in Fig. 7A corresponds essentially to the example already in the Figures 6A and 6B is indicated. The recesses 106, which surround the punching slots 102, here have a nearly rectangular shape. The total area GFV of all depressions 106 (without the total area of the punching slots 102, 102 ') is smaller here than the total area GFN, which lies at the normal level of the (main) plane E. The following applies: GFV <GFN.

The example in Fig. 7B differs from the example in Fig. 7A in that on the one hand the recesses 106, which surround the punching slots 102, a slightly oval Have shape. In addition, the area of these recesses 106 is greater than in Fig. 7A , Additionally or alternatively, further depressions may be provided on the rear side 101. In Fig. 7B it is indicated that, for example, a depression 108 can be located centrally between in each case four punched slots 102, 102 '. This sink 108 may be of any shape that may be produced by stamping, deep drawing, stamping, pressing, hammering, or a similar forming process. By increasing the area of the recesses 106 and adding further depressions in the form of depressions 108, the ratio between the total area GFV of all recesses 106, 108 and the total area GFN, which is at the normal level of the (main 5) level E, is changed. Here can thus apply: GFV = GFN.

In order to further improve the delay of the air flow L1 on the back 101, ie to increase the residence time of the air flow L1, a mat (eg a nonwoven) can be positioned on this back 101 in addition to the depressions 106 and / or depressions 108. This mat can be placed loose in the discharge box 20 or fixed on the back 101. Such a mat can be used in all described embodiments. These measures alone or together lead to an enlargement of the
As a result, the heat transfer, that is to say the heat exchange, between the ventilation element 100 and the air flow L1 can be improved. On the one hand, the air flow L1 becomes something preheated before it enters the room 1, and on the other hand, the Lüftungslement 100 heat is removed.

Among other things, the strength and the direction (here, for example, directed perpendicular to the back 101) of the air flow L1, which is guided through an air supply 21 in the rear discharge box 20, an influence on the strength of the individual fine primary air flows L2 (also called Einzelelluftstöme here ), which exit through air passage openings 102 of a ventilation element 100. A schematic diagram is in Fig. 1B shown. In Fig. 1B is a single air passage opening 102 can be seen, which extends from the back 101 through the vent member 100 to the front 103. A portion of the air flow L1, which flows along the rear side 101, passes through the air passage opening 102 and thus passes as a primary air flow L2 in the space R. The different length arrows of the primary air flow L2 indicate the velocity vectors of this primary air flow L2. At its core, the velocity is greater than at the edge of punched slot 102. At the periphery, each of the fine primary airflows L2 induction induces additional airflows (referred to herein as secondary airflows), which in Fig. 1B labeled L3. That is, each of the fine primary air flows L2 entrains air from the space R, resulting in rapid mixing of the fresh air L1 with the indoor air. The total of the fine primary air flows L2 set in motion amount of air is always larger by the induced secondary air L3, while the speed increases with increasing Distance from the ventilation element 100 in the direction of space is becoming smaller.

When passing through the air passage openings 102 in the direction of the space R, a secondary air flow L3 is induced by induction from the primary air flow L2 at each of the air passage openings 102, as mentioned. Here it has been shown that there is a relationship between the entire edge length (punched slot circumference: U) of an air passage opening 102, the punched slot surface F of this air passage opening 102 and the induction effect. It turns out that a circular air passage opening has an unfavorable ratio of circumference to the surface.

It has already been mentioned that the punching slots 102, 102 'have a slot length L between 2 and 10 mm and a slot width W between 0.1 and 0.8 mm. With reference to the following Table 1, the extreme values resulting from these ranges are compared with a circular air passage opening with the same area.

The two extreme cases shown in the table indicate that, with the smallest possible slot area F = 0.1 mm ^2, the ratio R is approximately twice as large as in the case of a circular area with the same area F = 0.1 mm ² . To be exact, the R of the punch slot 102 here corresponds to 1.96 times the R of the circle. With the largest possible slot area F = 8 mm ² , the ratio R is about 2.15 times as large as in a circular area with the same area F = 8 mm ² . Table 1 Punching slot with L = 1 mm and W = 0.1 mm circle Punching slot with L = 10 mm and W = 0.8 mm circle Area (F) [mm ² ] 0.1 0.1 8th 8th Circumference (U) [mm] 2.2 1,121 21.6 10,027 R = U / F [1 / mm] 22 11.21 2.7 1.2533

The device 10 provides better results when the air flow L1 first undergoes a deflection or deflection after entering the outflow box 20 in order to "flow" as far as possible along the rear side 101 of the ventilation element 100 (as in FIG Fig. 1B indicated by the horizontal arrow L1), before the passage through the air passage openings 102 in the direction of the space 1 takes place. When distributing the air flow L1 over the entire rear side 101 of the ventilation element 100, the recesses 106 play a role. Among other things, these recesses 106 cause the air flow L1 not to "flow" too quickly over the rear side. If the air flow L1 "flows" too fast, then only a small temperature exchange between the air flow L1 and the ventilation element 100 can take place, as already described above mentioned. However, this temperature exchange is essential for the function as a ventilation device 10. The ventilation element 100 assumes by convection almost the temperature of the room 1 at. If now a colder to L1 air flow L1 with the venting element 100 comes into contact, because a quantity of heat Q is transferred from the venting element 100 to the air flow L1. The air flow L1 heats up and the ventilation element 100 cools down. It is therefore important here that the residence time of the colder air flow L1 on the rear side 101 of the ventilation element 100 is as large as possible. This is effected according to the invention inter alia by an interaction of the air flow L1 with the depressions 106. These recesses 106 cause a local swirling or braking of the air flow L1. In addition, they increase the effective surface area.

It is important that the back 101 is not too rough and not too smooth. Preferably, as in FIGS. 6A and 6B indicated, the recesses 106 offset by an offset V with respect to the level of the (main 5) plane E of the back 101 back. V is preferably 0.1-2 mm. In addition, the recesses 106 are preferably configured to surround each punch slot 102. The depressions 106 preferably have a surface (without the actual punching slot surface F), which corresponds to approximately 1 to 5 times the punched slot surface F. In Fig. 6B an embodiment is shown in which the surface of the recesses 106 corresponds to about 2 times the punch slot surface F.

In addition, it has been found that it plays a role how large the so-called free cross-section FQ per unit area of the ventilation element 100 is. If the free cross section FQ per unit area is too large, then the air flow L1 from the outflow box 20 passes through the air passage openings 102 almost unhindered and at a low flow rate. If the free cross section FQ per unit area is too small, an undesirable stowage effect occurs in the outflow box 20. Optimal for the present invention, a free cross-section FQ, which is in the range between 3 and 20%. When determining the free cross-section per unit area, edge areas and other areas that have no punched slots 102 are not taken into account. At the in Fig. 5A As shown, the total area GF would be calculated as follows: GF = T1 x B1. In this example, the total area GF comprises one hundred and twelve punching slots 102. The free cross section FQ in percent is thus calculated as follows: FQ = 100 × (112 × L × W) / GF.

A better mixing of the room air is achieved when the induction number of the ventilation device 10 is as large as possible. On the other hand, standards (eg SIA standard 382/1) should be adhered to, for example as regards the freedom of movement of such a ventilation device 10. With the known ventilation device 10 induction numbers of up to 10 can be achieved, which means that, for example, 1 m ³ primary air flow L2 moves about 10 times more room air.

Furthermore, the performance of the ventilation device 10 plays a major role, since the performance in principle has a direct relationship to the economy and the cost of a ventilation device 10, including all ancillary components.

Ventilation devices 10, which are supplied with an air flow L1 having a ΔT between 2 and 10 degrees Celsius, have proven particularly useful. In the present case, however, ΔT can be between 4 and 12 degrees Celsius. However, larger ΔT values can lead to unfavorable and unpleasant drafts in room 1.

The ventilation devices 10 are preferably dimensioned and the ancillaries are designed so that a power of over 50 m ³ / h per m ² area of the ventilation element 100 is achieved without a ΔT must be specified, which is greater than 18 degrees Celsius.

Preferably, a metal plate (e.g., chromium steel) having a thickness D between 0.5 and 2 mm is used as the venting member 100. Such a metal plate can be processed in the required manner by punching or slitting so that on the one hand the punching slots 102 and on the other hand, the recesses 106 are formed with the dimensions already given above.

In the present case, the term "punching" is used to describe a method in which a punching, cutting or slotting tool penetrates into the sheet material to produce the punching slots 102 there. When punching the Edge of the punching slots are trimmed, so as to produce the recesses 106 in one operation. The term "punching slot" is therefore not intended to be limited to slots made by classical stamping, but is intended to include slots made by cutting or slitting.

Preferably, in the various embodiments, a regular arrangement of the punching slots 102 is used with a line grid with a line spacing Z1 of 1 to 15 mm and with a column spacing of 1 to 10 mm. The column spacing preferably corresponds to the slot length L, as in FIG Figs. 5A and 5B can be seen. The column spacing may also be greater or smaller than the slot length L. Preferably, the column spacing is between 0.5 times L and 2 times L.

The punched slots 102 are preferably offset from each other as shown in the various figures. They can be arranged on "gap", as in Fig. 5B to recognize, but they can also partially overlap each other, as in Fig. 8 shown.

In order to make the ventilation element 100 visually appealing, it should be adjusted in color. Conventional painting processes and paints are not suitable, as there is a risk of adding the punched slots and thus adversely affecting the ventilation effect. Preferably, the venting element 100 is therefore coated with a fine layer powder to prevent clogging.

On the basis of various embodiments it is shown that the ventilation element 100 can be formed as a flat plate or trough or trough-shaped. In the Figures 1A and 3 a flat plate is used as a ventilation element 100 is used. In the Figures 2 and 4 are tray-shaped or trough-shaped embodiments shown. By pulling up or bending the edges of the ventilation element 100, the overall aesthetic impression can be improved.

The two embodiments of the FIGS. 1A and 2 differ essentially only by the shape of the ventilation elements 100 from each other. All other elements can be identical or similar. The air supply takes place here through an air supply channel 21 with at least one toward the rear side 101 of the vent member 100 facing air nozzle 22. These elements of the air supply are arranged so that an air flow through the air supply passage 21 and from there through the air nozzle (s) 22 in the Outflow box 20 can flow.

The two embodiments of the FIGS. 3 and 4 in turn, differ substantially only by the shape of the ventilation elements 100 from each other. In the FIGS. 3 and 4 Embodiments are shown in which the air supply is constructed somewhat differently. The air supply here comprises a Anströmkasten 23 with an air duct 25 and at least one air nozzle 24. These elements of the air supply are arranged so that an air flow through the air duct 25, for example laterally into the Anströmkasten 23 and from there through the air nozzle / n 24 in the Outflow box 20 can flow. In the outflow box 20, these two embodiments behave similar to the embodiments of the FIGS. 1A and 2 ,

The embodiments shown, in addition to the advantages already mentioned also have the advantage that they offer a very good acoustic damping. The good acoustic damping results from the self-absorbing effect of the planar ventilation element 100 with punched slots 102.

Due to the fact that the ventilation devices 10 according to the invention provide better performance (air introduction with greater undertemperatures) by the use of the areal ventilation elements 100 (based on the square meter of the areal ventilation elements 100), it is possible to build significantly smaller-area ventilation outflow surfaces which nevertheless remain in a room 1 produce the same cooling effect as ventilation systems with a large-area ventilation outflow surface or conventional air inlets with air outlets. If a conventional ventilation system e.g. with a maximum undertemperature of 8K draft-free (acc. to SIA 382/1), a ventilation device with appropriate slitting of the ventilation element can already feed approx. twice the power (low temperature 16 K) into the room without pulling.

Such ventilation devices 10 can be used in the ceiling, wall and floor area of a room 1.

The planar ventilation elements 100 can be used as an element of a cooling ceiling with activation, ie with water cooling, or as an element of a ventilation device 10, as described.

Although such ventilation devices have already brought a significant improvement, there is still a need to effectively air-condition even large rooms with the smallest possible cooling devices without causing disturbing drafts. Such ventilation devices should be used not only in the ceiling, wall and floor area but also in corner areas.

In broad studies, it has surprisingly been found that when using appropriately finely slotted ventilation elements, a greater performance is not necessarily related to a larger active surface, but a higher and still draft-free air supply while maintaining certain conditions with a reduction of the active surface can. This is achieved by an arrangement of at least one active and at least one inactive surface on the ventilation element in a defined geometric relationship, whereby a significantly higher surface load and temperature difference (ΔT) can be used without producing disturbing drafts. It is important to note that the active surfaces (O _A ) are not too large with respect to the width of an active surface area extending over the length of the ventilation element, so that sufficient room air from the sides becomes active Surface can flow. Only by such an arrangement, especially in larger areas by a change of active and inactive surface areas, an effect called "spraying" can be achieved, which adjusts itself when the pressure difference between outflow box and space to be ventilated is at least 17 to 20 Pa. It was found that it is only in such a flow box due to the narrow slots and limited by additional inactive surfaces exit surface (s) or inactive surfaces of the ventilation element on the one hand, a necessary overpressure is easily adjustable, and it by the interaction of the overpressure, the Arrangement of the active and inactive surfaces and the slot grid on the active surfaces, on the space-facing side of the ventilation element to an immediate and complete detachment of the flow just in the room also comes out, which is here referred to graphically as spraying. Due to the geometry, the supply air flow dissolves substantially perpendicular to the surface of the ventilation element and generates a high induction effect by entrainment of laterally nachströmenden room air. In this case, high throw lengths can be achieved and at the same time, probably by the small-scale change of nozzle-like high-speed out of the slots outflowing incoming air and between nachfliessender, swirled room air, drafts are avoided. For practical reasons and in order to avoid the draft air that nevertheless occurs when the pressure difference is too high, however, the limits mentioned below between 100 and 150 Pa pressure difference should not be exceeded.

In order to realize this, a ventilation device is used which, in the installed state, has a planar ventilation element with air passage openings which faces in the direction of the space, wherein a discharge box is arranged on a rear side of the ventilation element which is opposite to the spatial direction is provided with an air supply for supplying an air flow and the ventilation element in a known manner has a plurality of slots arranged in rows and columns slots as air passage openings. The slots each have a slot length (L) of 2 to 20 mm and a slot width (W) of 0.1 to 0.8 mm, preferably from 0.2 to 0.6 mm; The line spacing (Z1), ie the distance between the non-offset lines, is 1 mm to 15 mm. In this case, between each two with respect to the x-direction not offset lines approximately half the distance (Z1 / 2) with respect to the slot positions in the direction of the x-axis offset line are inserted. The offset can be of the order of approximately 1 to 2 slot lengths. In this case, the slot lengths and slot widths of the offset lines in the areas as indicated above may be different or equal to the dimensions of the slots in the non-offset lines. The column grid (S1), ie the distance between the columns, in particular between the columns of the same row height is 0.5 x L to 2 x L, ie 1 to 20 mm. The column spacings are preferably the same on both sides. Adjacent columns with staggered rows can be arranged flush or overlapping.

dabei bevorzugt $$4\mathrm{L}\le {\mathrm{x}}_{\mathrm{A}}\le 35\mathrm{L}\mathrm{.}$$

According to the invention, the ventilation element comprises at least one active surface area O _A and at least one inactive surface area O _I and for at least one characteristic dimension x _A , for example the length, width, height, diameter, etc. of the active surface area O _A : $$\mathrm{3}\mathrm{L}\le {\mathrm{x}}_{\mathrm{A}}\le \mathrm{50}\mathrm{L}.$$

preferred $$4\mathrm{L}\le {\mathrm{x}}_{\mathrm{A}}\le 35\mathrm{L}\mathrm{,}$$

dabei bevorzugt $$\mathrm{4}\mathrm{L}\le {\mathrm{x}}_{\mathrm{I}}\le \mathrm{35}\mathrm{L}\mathrm{.}$$

Under active surface area O _A here is a ventilation-active surface area, ie a surface with a grid as mentioned above, in the air can flow through the slot grid, while in inactive surface areas O _{I of} the slot grid either covered or not provided from the outset. Similar or also the same dimensions of a characteristic dimension x _I can be set for the inactive surface area: $$\mathrm{3}\mathrm{L}\le {\mathrm{x}}_{\mathrm{A}}\le \mathrm{50}\mathrm{L}.$$

preferred $$\mathrm{4}\mathrm{L}\le {\mathrm{x}}_{\mathrm{I}}\le \mathrm{35}\mathrm{L}\mathrm{,}$$

For the characteristic dimensions of the active surface area O _A and the inactive surface area O _I , the following dimensions, ie width of a rectangle, sides of a square, diameter of a circle, height of a cylindrical surface were determined in the examples: 6 mm ≦ (O _A or O _I ) ≤ 1000 mm, preferably 8 mm ≤ (O _A or O _I ) ≤ 350 mm.

The grid should comprise at least three rows and three columns, but preferably at least 4 rows and 4 columns. Therefore, the minimum width of each active element should have an appropriate width.

The rear side of the ventilation element can have a regular arrangement of depressions as described above, which are formed in the spatial direction with respect to the level of a rear plane (E) of the ventilation element.

The surface of the ventilation element may be flat, cylindrical or prismatic. Under zylinderisch and prismatic here only partially cylindrical or partially prismatic trained surfaces are understood, as for example. For the use of so-called Eckquellen, i. For example, quarter-cylinder ventilation devices that are used in a room corner, find use. With regard to the prismatic forms, reference should be made in particular to advantageous embodiments with regular hexagons or octagons or their semi- or quarter-prismatic embodiments.

The surface of the ventilation element may comprise alternately arranged active surface areas (O _A ) and inactive surface area (O _I ). Examples of these are strip-shaped, wave-shaped or checkerboard-like arrangements. Alternatively, multiple active surface areas (O _A ) or multiple inactive surface areas (O _I ) may be distributed in an inactive or active field on the surface of the vent element. For example. As rectangles or rhombohedron arranged active or inactive surface areas in an inactive or active field as circles, ellipses, three, four or other polygons, for example.

dabei bevorzugt $$\mathrm{0.25}\le {\mathrm{O}}_{\mathrm{A}}/{\mathrm{O}}_{\mathrm{I}}\le \mathrm{0.55}$$

The ratio of the active surface areas (O _A ) to the inactive surface area (O _I ) can be as follows: $$\mathrm{0.2}\le {\mathrm{O}}_{\mathrm{A}}/{\mathrm{O}}_{\mathrm{I}}\le \mathrm{0.6}.$$

preferred $$\mathrm{12:25}\le {\mathrm{O}}_{\mathrm{A}}/{\mathrm{O}}_{\mathrm{I}}\le \mathrm{12:55}$$

The device may be at least partially or as a whole cylindrical or prismatic, with each other in a direction of a cylinder or prism axis cylindrical or prismatic active surface areas (O _A ) of the ventilation element (100) alternate with cylindrical or prismatic inactive surface areas the height h _{A is} the characteristic size of the active surface area and the height h _{I is} the characteristic size of the inactive surface area. This embodiment is suitable, for example, for columnar, vertical or, for example, also for tubular devices which are installed parallel to a ceiling. The height of the cylindrical or prism-shaped active surface area can be 60 to 180 mm, preferably 100 to 140 mm. In the case of small heights of the cylinder-shaped or prism-shaped surface areas, these are also referred to below as annular or as rings.

Alternatively, an at least partially or as a whole cylindrical or prismatic device formed at least one cylinder segment or at least one prism segment of the surface of the ventilation element a continuous, or interrupted only at greater intervals active and / or a corresponding inactive surface area (O _A , O _I ) , For larger diameters, several alternating active and inactive surface areas can advantageously be used here be arranged along the circumference, parallel to the cylinder or prism axis.

The slot grid can be formed substantially on the entire surface of the ventilation element, which, as is familiar to the expert, edge areas, for example, be excluded for processing reasons, and the inactive surface areas (O _I ) of the ventilation element can be formed by planar covers.

The cover can be formed by a sheet of foil or a paint covering the slots and in principle be mounted on the inside or the room side facing the room side of the ventilation element. The sheet or foil may be glued or, in particular, simply clamped when attached to the inside. Thus, the cover may comprise an elastic, completely or partially cylindrical or wholly or partially prismatic curved foil or sheet, which is clamped or glued to the ventilation element in the device which is at least partially cylindrical or partially prismatic, for example.

In principle, in all embodiments, the ventilation element may comprise a metal plate with a thickness (D) of between 0.5 and 2 mm, or be manufactured as a whole from such a metal plate. The material may, for example, a sheet, for example. From electrolytically galvanized (ECG), stainless steel or aluminum. The slots can be introduced into the material as mentioned above, whereby a ratio (V) of the punch slot circumference (U) to the punch slot surface (F) is, for example, between 2.7 and 22 can. The free cross section (FQ) per unit area of the active surface O _{A of} the ventilation element can be in the range of 1 to 20%, preferably in the range of 2 to 10%. Furthermore, each punched slot can be surrounded by a depression and / or depressions can be provided between the punching slots, in each case on the side of the ventilation element facing the outflow box.

Furthermore, at least one further row of slots can be arranged between the rows of the grid in a half line spacing Z1 / 2. The slots of the further line can be offset relative to the x-axis, preferably being arranged offset symmetrically with respect to the slots of the two immediately adjacent lines. In this case, the slots of the rows and the slots of the further rows form an overlapping, flush or spaced-apart arrangement of columns. The slots of the further line can each have a slot length (L) between 2 and 10 mm and a slot width (W) between 0.1 and 0.8 mm and also have the same geometry as the slots of the adjacent rows.

The air supply of the ventilation device may comprise an air supply channel with at least one pointing in the direction of the rear of the ventilation element air nozzle, said elements of the air supply are arranged so that an air flow through the air supply channel and from there through the at least one air nozzle can flow into the outflow box.

Alternatively, the ventilation device can also be a Anströmkasten with air duct and at least as stated above an air nozzle, wherein these elements of the air supply are arranged so that an air flow through the air duct in the Anströmkasten and from there through the at least one air nozzle can flow into the outflow box. Anströmkasten and / or Abströmkasten may also be cylindrical or prismatic in cylinder or prism-shaped ventilation devices. For example. For example, a larger diameter / circumference cylinder or prismatic exhaust box may include a smaller diameter / circumference cylinder or prism shaped inflow case.

The present invention also includes a ventilator having a plurality of ventilation devices as set forth above.

Furthermore, the present invention also encompasses a method for operating a ventilation device or a ventilation device as explained above, the device having an air throughput of 100 to 2000 m ³ / h, preferably 500 to 1400 m ³ / h per square meter of active area is operated.

In such a method, the device can be operated with a pressure difference between the inside facing the outflow box and the space facing the outside of the planar ventilation element, wherein the pressure difference in a range of 17 to 150 Pa, thereby preferably adjusted from 20 to 100 Pa.

The induction number, ie the ratio of the entrained secondary air quantity to the imported primary air quantity in the near field, for example at a distance of 800 mm from the Surface, in particular of a central region of an active surface of the ventilation unit can be adjusted from 5 to 20, preferably from 10 to 15, which corresponds to a very high value. To determine the induction coefficient, the temperature quotient between the temperature of the supply air and the temperature of the mixed air (from room and supply air) was determined at a distance of 800 mm and related to the volume flow.

Due to the relatively high required minimum throughput to the corresponding pressure difference and thus ensure the desired spray effect, inventive ventilation devices are particularly well suited for constant continuous operation. Good controllability can be achieved if, for example, a ventilation device comprising several ventilation devices is operated in such a way that, depending on the desired ventilation requirement, individual ventilation devices are switched on or off.

It should be expressly noted that the invention includes all here not explicitly mentioned in examples combinations of individual features that are disclosed only in connection with another embodiment, as long as such a combination would not be recognized from the outset as contrary to the skilled person. Likewise, the invention also relates to corresponding combinations of an inventive feature with one of CH 702 748 characteristic inherited as state of the art.

• Fig. 9A eine schematische Schnittansicht einer rohrförmigen Lüftungsvorrichtung des Standes der Technik;
• Fig. 9B und 9C jeweils eine schematische Schnittansicht einer rohrförmigen erfindungsgemässen Lüftungsvorrichtung;
• Fig. 10A eine schematische Ansicht einer säulenförmigen Lüftungsvorrichtung des Standes der Technik;
• Fig. 10B eine schematische Ansicht einer säulenförmigen erfindungsgemässen Lüftungsvorrichtung;
• Fig. 11A bis 11C verschiedene schematische Ausführungsformen eines flächigen Lüftungselements für eine Lüftungsvorrichtung;
• Fig. 12 eine schematische Ausführung einer rohrförmigen Lüftungsvorrichtung mit einer zylindersegmentförmigen und mehreren ringförmigen inaktiven Oberflächen;
• Fig. 13 ein Ausführungsbeispiel einer rohrförmigen Lüftungsvorrichtung mit ringförmigen aktiven und inaktiven Oberflächen;
• Fig. 14 ein Ausführungsbeispiel einer rohrförmigen Lüftungsvorrichtung mit einer zylindersegmentförmigen und mehreren ringförmigen inaktiven Oberflächen;
• Fig. 15-19 verschiedene Ausführung von säulenförmigen Lüftungsvorrichtung mit ring- oder zylinderförmigen aktiven bzw. inaktiven Oberflächen;

In the following, the present invention will be described with reference to various embodiments with reference to FIGS FIGS. 9 to 12 and Table 2 and 3 described. Showing:

• Fig. 9A a schematic sectional view of a tubular ventilation device of the prior art;
• Figs. 9B and 9C in each case a schematic sectional view of a tubular ventilation device according to the invention;
• Fig. 10A a schematic view of a columnar ventilation device of the prior art;
• Fig. 10B a schematic view of a columnar inventive ventilation device;
• Figs. 11A to 11C various schematic embodiments of a planar ventilation element for a ventilation device;
• Fig. 12 a schematic embodiment of a tubular ventilation device with a cylinder-segment-shaped and a plurality of annular inactive surfaces;
• Fig. 13 an embodiment of a tubular ventilation device with annular active and inactive surfaces;
• Fig. 14 an embodiment of a tubular ventilation device with a cylinder-segment-shaped and a plurality of annular inactive surfaces;
• Fig. 15-19 various embodiment of columnar ventilation device with annular or cylindrical active or inactive surfaces;

Fig. 9A schematically shows the flow pattern of a tubular, mounted under a ceiling ventilation device 10 of the prior art, in the substantially, ie apart from the cover by Briden and nozzle, the entire cylindrical surface as the active surface O _A with a as above described slot grid with a slot spacing (Z1) of 10 mm (slot length = 3 mm, slot width = 0.3 mm) and a column spacing (S1) of 3 mm is formed.

Between each two lines aligned in columns was, as in all experiments, analogous to FIG. 5A, B another row of slots of the same geometry offset by a column arranged flush. The slot grid was oriented transversely to the flow direction with respect to the longitudinal axis (3 mm) of the slots. The slot openings were inclined relative to the surface of the ventilation element (depth direction, for example. Perpendicular to the plane of the drawing of the drawing 5A, B)) slightly against the axial main flow direction of the tube.

The experiments were carried out in a large-scale laboratory with 3'350 mm room height and a base area of 4'200 x 6'500 mm, and filmed with a video camera. For this purpose, a ventilation pipe with a length of two meters and a diameter of 200 mm was mounted horizontally to the ceiling at a suspension height H (ie the distance between the center of the pipe and the ceiling). The room temperature was set at about 26 ° C, the supply air by about 5 K lower. The supply air flow was regulated with an iris diaphragm (nominal diameter 125 mm) at the inlet air inlet of the pipe. In position 1, the iris diaphragm is completely 100% open. The corresponding volume flow V ' _ZUL adjusts itself to this as a function of the temperatures of supply air and room air and the exhaust air volume V' _ABL , which will not be discussed in detail here. Further details of the experiments carried out with horizontally suspended ceiling tube can Table 2, as well as with respect to the geometric arrangement of the free and hidden surfaces of the Figures 9B and 9C , or to experiment 20 or 21 den Figures 13 or 14 are removed. The other details given in the table relate to the following information: The test number; the suspension height; in each case from the ceiling to the center of the pipe / axis, measured in millimeters; the covered, in this case masked area (area in m ² ); the additional area covered by bridges or sockets; the free area; the corresponding surface load in m ³ / (h * m ² ), which results from the likewise indicated volume flow V '(in m ³ / h) of the supply air; the setting of the iris diaphragm; the supply air T _ZUL and the room temperature T _room in ° C; the difference temperature ΔT between space and supply air in K; the pressure difference ΔP _ST between the overpressure inside the pipe and in the room; the measurement heights for measuring the air velocity in space measured in cm from the floor level of the test room; and the corresponding air _speeds V _AIR in mm / s (mean over 180 seconds).

It turned out that, in the case of a tube 10 with a substantially completely active cylindrical surface, first, as in FIG Fig. 9A sketched, a substantially vertically downwardly directed flow L6 forms, which spreads laterally only in the bottom area, which can cause noticeable drafts both under the ventilation and in the floor area. For example, velocities of between 185 and 300 mm / s were measured at a height of 180 cm at a measuring tree positioned below the pipe 10 at a distance from the pipe axis. The distance was set so that the measuring tree stood in a previously determined by flue gas tests area of the largest cold air drop (highest flow velocity). Tests numbered 1, 2, 6, 7 and 9 refer to such an experimental setup.

Alternatively, in experiments 3, 4, 5, 8, 10, 11, 12 and 13, the lower half of the cylinder was coated with a film analogous to FIG. 9B , taped as indicated in the table. Thus, the respective circular arc k _A , k _I can be regarded as the characteristic or characteristic variable for the active or inactive surface area O _A or O _I. The flow pattern in experiments 3, 4, 5, and 10 remained essentially unchanged. In experiments with a high surface load of 546 m ³ / h * m ² , or from an overpressure in the pipe of at least 17 Pa (test number 11), however, it surprisingly came to form a very different flow behavior of the emerging in the room supply air flow L7 or L7 ', as in the Figs. 9B and 9C shown. In this case, the air flow from the slots, not shown here, as sprayed from nozzles under the ceiling or laterally into the room. The room air is thereby entrained by the supply air as indicated by the arrows L8 and L8 '. This mixture of supply air and room air then sinks over a large surface area relatively low speed. With otherwise the same experimental arrangement, the flow rate in 180 cm height is clear, for example. From 210 to 140 mm / s (see experiment 8 to experiment with the prior art arrangement in experiment 7) or, for example. From 300 to a range between 110 and 200 mm / s (compare Experiments 11, 12, 13, to prior art experiment in experiment 9).

In experiments 11 and 12, as in Fig. 9C represented still the upper semi-cylindrical active surface area divided by an additionally arranged therebetween cover 11, which is the characteristic size k _A 'for the active surface and the characteristic sizes k _I and k _I ' for the inactive surface. It was achieved for attempt 11 a throw of one meter. With the same geometry and significantly increased pressure, or surface load as shown in experiment 12, the throw could be doubled to 2 m, but at all measuring heights too high air velocity and thus drafts occurred. In contrast, experiment 13 shows a very favorable adjustment of the pressure difference for an identical with experiment 10 arrangement, ie coverage of the lower cylinder segment. Here, a throw of 1.3 m without any drafts was achieved. The throw height from the tube axis was 12 and 13 at 0.6 m. This size corresponds to the height component of the throwing distance measured from the tube axis.

In Experiment 20, instead of covering one or more circular segments of a tube having the same dimensions as in the previous experiments, a plurality of substantially annular inactive surfaces were created by masking the surface of the venting member 100. It was like in FIG. 13 4, a total of 44 free rings of 20 mm width active surface left free, which are separated by strips inactive surface area, inactive surfaces of the ventilation element 100 are here and in the FIGS. 14 to 19 black, active white. The latter have partially as shown a different ring thickness, see FIG. 13 , Surprisingly, it turns out that such an arrangement with unusually high form and surface load can be driven, with only in the ground-level measuring range, a slight exceeding of normative for drafts set limit of 150 mm / s was measured. The air temperature at the three measuring points was much closer to the room air, from which a very high induction can already be deduced. It should be remembered here that the measuring points were set up at the locations with the highest flow velocity, see above.

Similar to experiment 20 is also, as in FIG. 14 shown, the arrangement for experiment 21, except that in this case additionally in the lowermost region of the tube, a pipe segment is covered with a circular arc of 140 mm in length in a respect to the suspension symmetrical area. In such an arrangement, the ventilation device with even higher Surface pressure and thus set higher pressure difference without, in any area of the room, the normatively permissible air velocity was exceeded.

Fig. 10A shows the schematic flow pattern of a columnar, vertical ventilation device 10 of the prior art, determined in a cloud chamber, in which the major part of the cylindrical surface is designed as an active surface O _A with a slot grid as described above. Clearly visible is a tree-shaped flow pattern L4, which develops here symmetrically around the device. Details for such a test with a 2 m high column with 200 mm diameter are Table 3, Experiment 16, the geometric arrangement of the Figures 16 refer to. In this case, the ventilation arrangement 10 consists of a base plate 26, a 150 mm high base 27, the columnar ventilation element 100 set thereon and the air supply not shown here. The flow rate measured at a distance of half a meter from the tube, at 130 and 180 cm, is very low at 30 mm / s, see the column "Air velocity in the room", and thus the ventilation is inadequate. Due to the relatively rapid drop in this much cooler, poorly mixed supply air, can also develop at a relatively low ventilation performance as perceived as unpleasant pulling behavior near the ground, despite the ventilation effect in the rest of the room is very low.

In contrast, in Fig. 10B schematically shows the flow pattern of a columnar, vertical ventilation device 10 according to the invention, in which cylindrical active and inactive surface areas O _A , O _I are annularly arranged in alternating sequence. By due to the partial coverage of the cylindrical surface caused increased pressure inside the device, the nozzle effect of the slot grid, under otherwise identical experimental conditions significantly increased, thereby, in combination with the corresponding geometric dimensions, in particular the active surface areas O _A , the supply air L5 completely and substantially perpendicular to the active cylinder surface O _A replaces and at the same time entrains room air in the form of a vortex flow L6 from the adjacent areas. As characteristic dimensions in this case the heights of the cylinders with active and inactive surface h _A and h _I can be considered. In experiments 14 and 15, with a likewise 2 m high column, h _A and h _{I were} each 120 mm. Geometric details are in FIG. 15 shown. In experiment 15, in which a similar surface load was set as in experiment 20, this also sets a similarly favorable behavior and pressure difference. Even with the lower set surface load of the test 14, the results are appealing, even if the cooling capacity is lower.

Further experiments with slightly different geometries show FIGS. 17 to 19 their results are described in the corresponding experiments 17 to 19 of Table 3. Again, each two meters long tubes with a diameter of 200 mm and an identical slot grid are used as ventilation elements and the corresponding area ratios and geometries are produced by masking the slot grid with foil. With the exception of the suspension height not used here, Table 3 contains details of the same settings and measured variables as described in detail in Table 2.

The geometry of the grid was chosen as described above. Only the slot opening were, unlike the experiments indicated in Table 2, slightly inclined with respect to the surface of the ventilation element against the axial main flow direction of the tube.

The results of experiment 17 with a columnar vent with continuous active surface in the upper half and solid inactive surface in the lower half, as in FIG. 17 shown, however, are less satisfactory. In particular, it comes in the lower area to a slight if exceeding the permissible air velocity.

On the other hand offer as in the Figures 18 and 19 shown configurations of the ventilation element in which only the lower or only the upper half of the surface is provided with annular active surface areas, while the other half of the surface is inactive, the ability to operate the ventilation device 10 with very high surface load and thus high pressure difference, what the vertical spread of the supply air from the surface of the ventilation element in the room, especially arranged transversely to the supply air flow in the pipe Slot grid favors. This phenomenon applies to all ventilating devices or methods according to the invention, just as fundamentally all the features shown in connection with an embodiment or with reference to an exemplary embodiment can also be combined with other embodiments or examples, unless this is obviously obviously contradictory to the person skilled in the art.

Furthermore, it is generally unnecessary to provide a flow box with conventional pipe dimensions, but rather it suffices, depending on the pipe length, to provide the power supply from one side or, for example, a T-shape from the center, so that there is an axis-parallel main flow in the interior of the pipe adjusts from which branched away by the slot pattern partial flows branch off laterally, wherein the tube simultaneously forms the outflow box. Alternatively, in particular with large diameters, it is also possible to provide an inflow box arranged, for example, along the tube axis or in the region of a segment with an inactive surface.

It should be noted that in no case could a comparable favorable behavior be achieved with a continuous active surface even if higher pressure differences and / or surface loads were set (see, for example, Experiment 16). Obviously, the correct adjustment of the ratio of the active to the inactive surface and the arrangement geometry, ie the arrangement of the active and inactive surfaces, contributes in particular to large areas Ventilation devices essential to the formation of a favorable flow pattern in the room.

It should be noted that the same basic ventilation device was used for all experiments whose cylindrical ventilation element 100 a w.o. has described slot grid with aligned parallel to the cylinder axis slots. The difference in the flow behavior with otherwise identical experimental parameters thus resulted only from the different coverage / arrangement of the active or inactive surfaces, which took place here merely for practical reasons by external masking of different surface areas with adhesive film.

In general, it may be noted that in any tubular venting device, the use of a venting element (100) having a plurality of alternately arranged annular or semi-annular active and inactive surface areas has proven to be advantageous in operation. Thus, a greater pressure difference between the interior of the tube and the environment can be built, which allows the occurrence of a spray effect with increased throw and induction and also a greater cooling / heating capacity. This applies not only to circular, cylindrical or polyhedral raw cross sections, but also to corresponding half or quarter pipe cross sections, as used, for example, for ventilation device which can be operated on a wall or a corner of the room.

Further examples of the distribution of surfaces, especially for large-area ventilation devices with a total area, for example, greater than 1 or 2 m ² , are in Figs. 11A to 11C shown.

So shows Fig. 11C an arrangement circular active surface area O _A in an inactive field O _{I of} a planar ventilation element 100, which may be formed in a plane or, for example, as a quarter, half or full cylinder. As a characteristic dimension of the active surface area O _A , the diameter d _A can be considered. As a characteristic size of the inactive surface can be considered unspecified diameter (double arrow) of the dashed, inserted between the active surfaces circle. It should be noted that the indication of a characteristic size or dimension x _I for the inactive surface area can only be advantageous if the area of the ventilation element in the direction of both surface coordinates is greater than the characteristic size or dimension x _{A of} the active surface area. In particular, greater than twice the dimension x _{A of} the active surface area.

Fig. 11B shows a corresponding ventilation element 100 with alternately strip-shaped active and inactive surface areas O _A and O _I with corresponding characteristic dimensions b _A , b _I. Fig. 11C shows a checkerboard-like arrangement, but in which the inactive surface areas O _I in two directions are strip-shaped continuously formed and form intersecting, here orthogonal corridors through which the room air can flow particularly easily in the direction of the active surface areas O _A. This allows the induction effect above all else be further improved with large-area ventilation elements 100. Characteristic dimensions here are the side length (s) s _{A of} the active area O _A and the corridor width (n) s _{I of} the inactive areas O _I. Of course, such an effect can also be combined with corridors running obliquely against one another and / or with elliptical, in particular circular, formed active surface areas.

Fig. 12 shows a further tubular inventive ventilation device 10 in which the inactive surface areas O _{I of} the ventilation element 100 are formed in a continuous strip in two directions and form intersecting corridors. The ventilation device hangs horizontally under a ceiling. Such a design is advantageous in the case of larger pipe diameters, for example from 300 mm and / or large temperature differences, between supply air and room air (for example .gtoreq.3 K), in particular given a corresponding under temperature of the supply air and greater cooling capacity. In this case, the slot grid are covered or not executed in the lower part of the tube, which results in a more favorable distribution of the supply air, in particular a supply air with low temperature compared to the room air. Analogously, such tubes can also be formed as vertical columns, wherein the inactive to the tube axis parallelel surface, depending on the site eg. In several narrower strips distributed over the circumference can be arranged.

In general, it is advantageous for pipes to form the slot patterns in such a way that a higher dynamic pressure forms inside the tube due to the volume flow. that these are transversely, in particular perpendicular to the flow direction, since thereby a rapid detachment of the flow from the pipe surface into the space, for example, substantially perpendicular to the outer surface facing the space of the ventilation element 100, is facilitated. The slots can also be inclined with respect to the surface of the ventilation element either vertically or, as often unavoidable for manufacturing reasons, slightly in (ie angle slightly less than 90 degrees) or counter (ie angle slightly greater than 90 degrees) the axially directed Hauptstömungsrichtung ( for example, in a range of 0 to 10 degrees, ie, for example, 80 to 110 degrees from the surface).

The orientation of the slit turret generally plays a lesser role in box-shaped venting devices, especially if they additionally have a flow-in box 23, which already diverts the airflow from a pipe axis-parallel alignment in the direction of the inner surface of the venting element. On the other hand, in the case of tubular or columnar ventilation elements, or quite generally, with supply air flow guided essentially parallel to the inner surface of the ventilation element and parallel alignment of the longitudinal axis of the slots, an undesired flat or even surface-parallel exit of the supply air into the space may occur Detachment of the air flow difficult and the ventilation performance deteriorates markedly. In particular, this causes a smaller throw and lower induction.

In exclusively downwardly directed flows, it has proved to be favorable to provide more and / or larger distances between the active surface areas, ie to increase the proportion of the inactive surface. For example, in the case of a striped arrangement of the active and inactive surfaces of a cooling ceiling, the characteristic dimension x _I , in this case the width b _{I of} the stripes of the inactive surface O _{I, can be selected} in a range from 500 to 1000 mm, while the width of the active surface area O _{A is selected} in a range of 8 to 350 mm. In addition, the active still, for example, as detailed above, be interrupted by inactive areas. Table 2 Vers.Nr. Suspension height tube axis mm Abgekl. Area O _I m ² Additionally dil. O _I m ² Free area O _A m ² Wing loading m ³ / h * m ² Aperture 125mm V ' _ZUL m ³ / h T _room ° C T _ZUL ° C T _ABL ° C ΔT _{ZUL space} K ΔP _ST Pa _Measuring height v _AIR cm v _AIR mm / s T _measuring ° C 1 150 0 12:16 1099 120.1 4 132 25.90 20:40 - 5:50 - 180 200 - 130 160 10 100 2 150 0 12:16 1099 120.1 4 132 25.95 20.95 - 5:00 - 180 185 - 130 180 10 100 3 150 0628 12:08 0.5495 240.2 4 132 26.00 21:00 - 5:00 - 180 115 - 130 115 10 100 4 150 0628 12:08 0.5495 240.2 4 132 26.00 20:50 - 5:50 5 180 140 - 130 140 10 115 5 150 0628 12:08 0.5495 414.9 2 228 26.00 21:20 - 4.80 11 180 145 - 130 140 10 85 6 150 0 12:16 1099 207.5 2 228 26.00 21:00 - 5:00 - 180 220 - 130 160 10 160 7 150 0 12:16 1099 273.0 1 300 26.00 20:15 - 5.85 5 180 210 - 130 210 10 160 8th 150 0628 12:08 0.5495 546.0 1 300 26.10 20.70 - 5:40 20 180 140 - 130 110 10 110 9 950 0 12:16 1099 273.0 1 300 26.20 20.80 - 5:40 - 180 300 - 130 300 10 125 10 950 0628 12:08 0.5495 546.0 1 300 26.20 20:50 - 5.70 - 180 100 - 130 100 10 170 11 950 0728 12:07 0463 594.0 1 275 26.00 20:50 - 5:50 17 180 110 - 130 140 10 90 12 950 0728 12:07 0463 853.1 1 395 25.90 20:50 - 5:40 32 180 200 - 130 160 10 180 13 950 0628 12:08 0.5495 718.8 1 395 25.90 20:40 - 5:50 26 180 140 - 130 110 10 120 20 950 0.71 00:00 12:55 836.4 1 460 26.00 20:50 26.40 5:50 40 180 145 25.10 130 110 25.25 10 165 24.70 21 950 0.83 00:00 12:43 1046.5 1 450 25.80 20:40 25.60 5:40 60 180 130 25.25 130 90 25.40 10 120 25.10 Vers.Nr. Abgekl. Area O _I m ² Additionally dil. O _I m ² Free area O _A m ² Wing loading m ³ / h * m ² Aperture D = 125 mm V ' _ZUL m ³ / h V ' _ABL m ³ / h T _room ° C T _ZUL ° C T _ABL ° C ΔT _{ZUL space} K ΔP _ST Pa _Measuring height v _AIR cm v _AIR mm / s T _measuring ° C 14 0.65 00:00 0606 651.8 1 395 395 25.80 20.60 - 5.20 25 180 50 25.40 130 50 25.10 10 100 24.00 15 0.65 00:00 0606 808.6 1 490 490 25.85 20.70 - 5.15 37 180 50 25.30 130 40 25.10 10 120 23.80 16 0 12:10 1156 423.9 1 490 490 25.80 20.60 - 5.20 16 180 30 25.50 130 30 25.15 10 110 22.90 17 0.63 12:05 0576 798.6 1 460 460 26.00 20:50 26.30 5:50 40 180 30 26.20 130 110 25.50 10 155 24.15 18 0.86 12:05 0346 1242.8 1 430 460 25.80 20.60 26.30 5.20 80 180 45 25.90 130 125 25.20 10 125 24.55 19 0.86 12:05 0346 1242.8 1 430 460 26.00 20.60 26.50 5:40 80 180 25 26.20 130 35 26.00 10 90 24.40 breather 10 Abströmkasten 20 air supply 21 air nozzle 22 Anströmkasten 23 air nozzle 24 air duct 25 baseplate 26 base 27 planar ventilation element 100 back 101 punching slots 102 front 103 web 104 Transition area 105 deepening 106 surface sections 107 depression 108 width B1 thickness D rearward (main5) level e Punching slot surface F free cross section FQ total area GF Total area. all wells FV Total area, which is at the normal level GFN slot length L airflow L1, ... L8 Primary air flow L2 Induction air flow L3 Active, inactive surface O _A , O _I room R depth T1 Punching slot extent U slot width W offset V Characteristic sizes of the active, inactive surface (s) x _A , x _I Characteristic. Height _{Active / Inactive} h _A , h _I Characteristic. _{Arcs Active / Inactive} k _A , k _I

Claims (26)

Ventilation device (10) for mounting in a room (1), wherein the ventilation device (10) in the mounted state has a space-oriented planar ventilation element (100) with air passage openings and wherein an outflow box (20) on a rear side opposite the spatial direction (101) the ventilation element (100) is provided with an air supply (21, 22, 23, 24, 25) for supplying an air flow, and the ventilation element (100) has a plurality of slots arranged in a row (109) and columns (110) (102) as air passage openings and the slots (102) each have a slot length (L) between 2 and 10 mm and a slot width (W) between 0.1 and 0.8 mm, wherein the line grid (Z1) 1 mm to 15 mm and the column grid (S1) is 0.5 × L to 2 × L, characterized in that the ventilation element (100) comprises at least one active surface area (O _A ) and at least one inactive surface area (O _I ) and un d for at least one characteristic dimension x _{A of} the active surface area (O _A ): $$\mathrm{3}\mathrm{L}\le {\mathrm{x}}_{\mathrm{A}}\le \mathrm{50}\mathrm{L}\mathrm{,}$$

Ventilation device (10) according to claim 1, characterized in that for at least one characteristic dimension x _{I of} the at least one inactive surface area is: $$\mathrm{3}\mathrm{L}\le {\mathrm{x}}_{\mathrm{I}}\le \mathrm{50}\mathrm{L}\mathrm{,}$$

Ventilation device (10) according to any one of the preceding claims, characterized in that the grid comprises at least three rows and three columns. Ventilation device (10) according to any one of the preceding claims, characterized in that the surface the ventilation element is flat, cylindrical or prismatic. Ventilation device (10) according to any one of the preceding claims, characterized in that the device comprises a plurality of on the surface of the ventilation element (100) distributed active surface areas (O _A ) and / or more inactive surface area (O _I ). Ventilation device (10) according to claim 5, characterized in that the surface of the ventilation element (100) alternately arranged active surface areas (O _A ) and inactive surface area (O _I ). Ventilation device (10) according to one of the preceding claims, characterized in that for the ratio of the active surface area, or the active surface areas (O _A ) to the inactive surface area (O _I ), or to the inactive surface areas, the following applies: $$\mathrm{0.2}\le {\mathrm{O}}_{\mathrm{A}}/{\mathrm{O}}_{\mathrm{I}}\le \mathrm{0.6.}$$

Ventilation device (10) according to any one of the preceding claims, characterized in that the device is cylindrical or prismatic, wherein at least one cylinder segment or at least one prism segment of the surface of the ventilation element (100) has an active surface area (O _A ). Ventilation device (10) according to one of claims 1 to 6, characterized in that the device is cylindrical or prismatic, with each other in one direction of a cylinder or prism axis cylindrical or prismatic active surface areas (O _A ) of the ventilation element (100). alternate with cylindrical or prismatic inactive surface areas where the height h _{A is} the characteristic size of the active surface area and the height h _{I is} the characteristic size of the inactive surface area. Ventilation device (10) according to claim 8, characterized in that the height of the cylinder or prismatic active surface area is 60 to 180 mm. Ventilation device (10) according to any one of the preceding claims, characterized in that the slot grid is formed substantially on the entire surface of the ventilation element (100), and the one or more inactive surface areas (O _I ) of the ventilation element (100) are formed by planar covers , Ventilation device (10) according to claim 10, characterized in that the cover comprises a sheet of foil or a paint covering the slots. Ventilation device (10) according to any one of claims 7 to 11, characterized in that the cover comprises an elastic wholly or partially cylindrical or wholly or partially prismatic curved foil or sheet, which in the cylindrically or prismatically formed device (10) to the ventilation element (100) clamped and / or glued. Ventilation device (10) according to one of the preceding claims, characterized in that a metal plate with a thickness (D) between 0.5 and 2 mm serves as a ventilation element (100). Ventilation device (10) according to any one of the preceding claims, characterized in that each punching slot (102) has a ratio (V) of punching slot circumference (U) to punching slot surface (F), which lies between 2.7 and 22. Ventilation device (10) according to one of the preceding claims, characterized in that between the rows of the grid at a distance Z1 / 2 at least one further row of slots (102 ') is arranged. Ventilation device (10) according to claim 16, characterized in that the slots (102 ') of the further line offset with respect to the x-axis, while preferably arranged symmetrically offset from the slots (102) of the two adjacent lines. Ventilation device (10) according to claim 16 or 17, characterized in that the slots (102) of the lines and the slots (102 ') of the further lines form an overlapping, flush or spaced arrangement of columns. Ventilation device (10) according to one of claims 16 to 18, characterized in that the slots (102 ') of the further row each have a slot length (L) between 2 and 10 mm and a slot width (W) between 0.1 and 0.8 mm. Ventilation device (10) according to any one of claims 16 to 17, characterized in that the slots of the rows (102) and the slots (102 ') of the at least one further row have the same geometry. Ventilation device (10) according to any one of the preceding claims, characterized in that the ventilation element (100) has a free cross-section (FQ) per unit area of the ventilation element (100), which is in the range between 3 and 20%. Ventilation device according to one of the preceding claims, characterized in that the ventilation element (100) a plurality of alternately arranged ring or having partially annular active and inactive surface areas. Ventilation device with a plurality of ventilation devices (10) according to one of claims 1 to 17. A method of operating a ventilation device (10) according to any one of claims 1 to 22, characterized in that the device is operated with an air flow rate of 100 to 2,000 m ³ / h per square meter of active area. A method according to claim 24, characterized in that the device is operated with a pressure difference between the inside and outside of the planar ventilation element of 17 to 150 Pa. Method according to one of claims 24 or 25, characterized in that the device is operated with an induction number of 5 to 20.

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