CH714025A1 - Ventilation device. - Google Patents

Abstract

Ventilation device for installation in a room, wherein the ventilation device in the mounted state has a space-oriented planar ventilation element (100) with air passage openings and wherein an outflow box on one of the spatial direction opposite rear side of the ventilation element (100) with an air supply (21, 22; 24, 25) is provided for supplying an air flow and the ventilation element (100) has a plurality of rows and columns in rows comprising columns slots (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) 0.5 x L to 2 x L, wherein the ventilation element (100) at least one active surface area and at least one inactive surface area, and for at least one characteristic dimension x A of the active surface range: 3 L ≤ x A ≤ 50 L.

Description

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 [0002] Induction is understood to mean the proportion of room air that is moved or entrained by the primary air flow supplied by the ventilation device. An induction number of 10 means that, for example, I m ³ moves primary air flow by a factor of 10, i.e. 10 m ^3, room air. 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 (e.g. the Swiss SIA standard 382/1, corresponds to EN 13779) should be observed in order to ensure that such a ventilation device is draft-free.

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

Area load is understood to mean the volume flow of the supply air per time and flowed through active area in m ³ / (h. M ² ).

An active surface is understood to mean a surface of a ventilation element which is provided throughout with a slot pattern, as described in more detail below, in particular a slot grid and is therefore air-permeable.

Inactive areas are air-impermeable areas of a ventilation element in which the slit pattern is either covered, closed or is not present.

Throwing distance is understood here to be the usual term in air conditioning technology, namely the distance from the outlet opening at which the supply air or mixed air flow there is already slowed to a speed of 0.25 m / s.

BACKGROUND OF THE INVENTION, PRIOR ART In the case of physical relationships which play a role in the design of a ventilation solution with ventilation holes, there are complex interrelationships. That is why the task is to offer appropriate solutions that are efficient and yet cost-effective. It is also about providing the greatest possible cooling capacity per room volume without causing disturbing drafts.

The invention builds on the knowledge of CH 702 748, the description and drawings of which are therefore an integral part of the present invention, and the most important findings of which are presented again below. The following was already recognized in the aforementioned Swiss patent:

- The strength and direction of the air flow, which is led 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 is first deflected or deflected after it has entered the outlet box, in order to "flow" as far as possible along the back of the ventilation element before it passes through the air outlet openings in the direction of the room.

When passing through the air passage openings in the direction of the room, a secondary air flow is induced at each of the air passage openings by induction from the primary air flow. It has been shown here that there is a relationship between the entire edge length (circumference) of an air passage opening, the area of this air passage opening and the induction effect. It was found that a circular air passage opening has a less favorable ratio of the circumference to the area than a slot.

- It was also found that it matters how large the so-called free cross-section per unit area of the ventilation element. If the free cross section per unit area is too large, the air flow from the outflow box passes through the air passage openings almost unhindered and at a low flow speed. If the free cross-section per unit area is too small, an undesirable accumulation effect occurs in the outflow box. A free cross-section is optimal, which is in the range 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 (e.g. the Swiss SIA standard 382/1) should be observed, which e.g. regarding the draft-free nature of such a ventilation device.

- Furthermore, the performance of the ventilation device plays a major role, since the performance is in principle directly related to the economy and the cost of a ventilation device.

First, details and advantages of this prior art are described using exemplary embodiments and partially with reference to the drawing. All figures are schematic and not to scale, and corresponding structural elements are provided with the same reference symbols in the various figures, even if they are designed differently in detail. It shows:

CH 714 025 A1

1A shows a schematic sectional view of a first embodiment of the prior art, which comprises an outflow box and a planar ventilation element;

1B shows a schematic enlarged detail of the ventilation element according to FIG. 1A with a punching slot;

2 shows a schematic sectional view of a second embodiment, which comprises an outflow box and a trough-shaped or trough-shaped ventilation element;

3 shows a schematic sectional view of a third embodiment of the invention, which comprises an inflow box and an outflow box as well as a planar ventilation element;

4 shows a schematic sectional view of a fourth embodiment of the invention, which comprises an inflow box and an outflow box as well as a trough-shaped or trough-shaped ventilation element;

5A is a schematic bottom view of a portion of a ventilation element;

5B is a schematic enlarged detail of the ventilation element according to FIG. 5A;

6A is a schematic sectional view of a ventilation element of the prior art;

FIG. 6B is a schematic bottom view of the ventilation element according to FIG. 6A;

7A shows a schematic bottom view of a further ventilation element with punching slots sitting on a “gap”;

7B shows a schematic view from below of a further ventilation element with punching slots sitting on a “gap”;

Fig. 8 is a schematic bottom view of another ventilation element with partially overlapping punch slots.

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

It is about ventilation devices 10 which are designed for mounting in a room 1. These ventilation devices 10 can be designed for ventilation, air conditioning and / or heating. These are preferably ventilation devices 10 for air conditioning, which cause a cooling effect in room 1 by supplying an air flow L1, the temperature of which is below the temperature of the room air in room 1.

[0013] In the assembled state, the ventilation device 10 comprises a flat ventilation element 100 with air passage openings facing in the spatial direction. The flat ventilation element 100 can extend parallel to a room ceiling. In this embodiment, an outflow box 20 is arranged on a rear side 101 of the ventilation element 100 opposite the spatial direction. An air supply 21, 22 for supplying an air flow L1 is provided in the interior of the outflow box 20. The ventilation element 100 comprises a plurality of punched 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, e.g. shown in Fig. 5B. The ratio between slot length L and slot width W is therefore between 2.5 and 100 in all embodiments. In addition, the rear 101 of the ventilation element 100 has a regular arrangement of depressions 106 (see, for example, FIG. 6B), which is opposite a rear (main ) Level E of the ventilation element 100 are formed in the spatial direction. This means that these recesses on the rear 101 are lower than the level of the rear (main) level E.

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

Areas in which punched slots 102, 102 'are located (shown as black areas in FIGS. 7A and 7B), recess 106 (shown as white areas in FIGS. 7A and 7B), which preferably have punched slots 102, 102' surround,

- Transitional areas 105 (indicated by dashed outline lines in FIGS. 7A and 7B), each of which characterize the transition between a depression 106 and a surface section 107 lying in the (main) plane E, and

- Struts 104 (also called surface sections 107), which lie in the (main) plane E. The surface sections 107, which are virtually at the normal level of the (main) plane E, are shown in FIGS. 7A and 7B as a hatched surface.

The example in FIG. 7A essentially corresponds to the example that has already been indicated in FIGS. 6A and 6B. The depressions 106, which surround the punching slots 102, have an almost rectangular shape here. 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 is at the normal level of the (main) plane E. The following applies here: GFV <GFN.

CH 714 025 A1 The example in FIG. 7B differs from the example in FIG. 7A in that on the one hand the depressions 106 which surround the punching slots 102 have a slightly oval shape. In addition, the area of these depressions 106 is larger than in FIG. 7A. Additionally or alternatively, further depressions can be provided on the rear side 101. In Fig. 7B it is indicated that e.g. a depression 108 can be located centrally between four punching slots 102, 102 '. This depression 108 can have any shape that can be produced by means of stamping, deep-drawing, embossing, pressing, hammering or a similar reshaping process. By increasing the area of the depressions 106 and adding further depressions in the form of depressions 108, the ratio between the total area GFV of all depressions 106, 108 and the total area GFN, which is at the normal level of the (main) level E, is changed. The following can therefore apply here: GFV = GFN.

To further improve the delay of air flow L1 on the rear 101, i.e. In order to increase the dwell time of the air flow L1, a mat (e.g. a fleece) can be positioned on this rear side 101 in addition to the depressions 106 and / or depressions 108. This mat can be placed loosely in the outflow box 20 or fixed on the back 101. Such a mat can be used in all of the described embodiments. These measures alone or together lead to an increase in the “surface friction” of the rear side 101. 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 is preheated somewhat before it enters the room 1, and on the other hand, heat is extracted from the ventilation element 100.

Among other things, the strength and the direction (here, for example, directed perpendicularly to the rear 101) of the air flow L1, which is guided by an air supply 21 into the rear outflow box 20, has an influence on the strength of the individual fine primary air flows L2 (here also called individual air flows) that exit through air passage openings 102 of a ventilation element 100. A schematic diagram is shown in Fig. 1B. A single air passage opening 102 can be seen in FIG. 1B, which extends from the rear 101 through the ventilation element 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 reaches the space R as the primary air flow L2. The arrows of the primary air flow L2 of different lengths indicate the velocity vectors of this primary air flow L2. In essence, the speed is greater than at the edge of the punching slot 102. In the edge region, each of the fine primary air flows L2 causes further air flows (referred to here as secondary air flows) by induction, which are labeled L3 in FIG. 1B. That each of the fine primary air flows L2 entrains air from the room R, which leads to a rapid mixing of the fresh air L1 with the room air. The total amount of air set in motion by the fine primary air flows L2 becomes ever greater as a result of the induced secondary air L3, while the speed decreases with increasing distance from the ventilation element 100 in the spatial direction.

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. It has been shown here that there is a connection between the entire edge length (punch slot circumference: U) of an air passage opening 102, the punch slot surface F of this air passage opening 102 and the induction effect. It can be seen that a circular air passage opening has an unfavorable ratio of the circumference to the area.

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. The following table 1 compares the extreme values that result from this range information with a circular air passage opening with the same area.

The two extreme cases, which are shown in the table, show that with the smallest possible slot area F = 0.1 mm ^2, the ratio R is approximately twice as large as with a circular area with the same area F = 0.1 mm ² . To be precise, the R of the punching slot 102 corresponds to 1.96 times the R of the circle. With the largest possible slot area F = 8 mm ² , the ratio R is approximately 2.15 times as large as with 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 if the air flow L1 only undergoes a deflection or deflection after entering the outflow box, in order to as far as possible along the rear 101 of the ventilation element 100

CH 714 025 A1 “flow” (as indicated by the horizontal arrow L1 in FIG. 1B) before it passes through the air passage openings 102 in the direction of the room 1. When distributing the air flow L1 over the entire rear 101 of the ventilation element 100, the depressions 106 play a role. Among other things, these depressions 106 ensure that the air flow L1 does not “flow” too quickly over the rear side. If the air flow L1 "flows" too quickly, then only a slight temperature exchange can take place between the air flow L1 and the ventilation element 100, as already mentioned above. However, this temperature exchange is essential for the function as a ventilation device 10. The ventilation element 100 almost takes on the temperature of the room 1 by convection. If an air flow L1 that is colder by TT now comes into contact with the ventilation element 100, then a quantity of heat Q passes from the ventilation 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 dwell time of the colder air flow L1 on the rear 101 of the ventilation element 100 is as long as possible. According to the invention, this is caused, inter alia, by an interaction of the air flow L1 with the depressions 106. These depressions 106 cause local swirling or braking of the air flow L1. They also increase the effective surface.

It is important that the back 101 is not too rough and not too smooth. As indicated in FIGS. 6A and 6B, the depressions 106 are preferably offset by an offset V from the level of the (main 5) plane E of the rear side 101. V is preferably 0.1-2 mm. In addition, the depressions 106 are preferably designed such that they surround each punching slot 102. The depressions 106 preferably have an area (without the actual punching slot area F) which corresponds approximately to 1-5 times the punching slot area F. An embodiment is shown in FIG. 6B, in which the area of the depressions 106 corresponds approximately to twice the punching slot area F.

It was also found that it matters 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 exits the outflow box 20 almost unhindered and at a low flow rate through the air passage openings 102. If the free cross section FQ per unit area is too small, an undesirable accumulation effect occurs in the outflow box 20. A free cross-section FQ which is in the range between 3 and 20% is optimal for the present invention. Edge areas and other areas that do not have punched slots 102 are not taken into account when determining the free cross section per unit area. In the example shown in FIG. 5A, 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 x (112 x L x W) / GF.

[0026] A better mixing of the room air is achieved if the induction number of the ventilation device 10 is as large as possible. On the other hand, standards (for example the SIA standard 382/1) should be observed, for example with regard to the draft-free nature 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, I m ³ primary air flow L2 moves about 10 times more room air. Furthermore, the performance of the ventilation device wines plays a major role, since the performance in principle has a direct connection to the economy and to the cost of a ventilation device 10 together with all auxiliary units.

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

The ventilation devices 10 are preferably dimensioned and the ancillary units are designed such that a capacity of over 50 m ³ / h per m ² area of the ventilation element 100 is achieved without having to specify a ΔΤ that is greater than 18 Centigrade.

Preferably, a metal plate (e.g. chrome steel) with a thickness D between 0.5 and 2 mm is used as the ventilation element 100. Such a metal plate can be machined in the required manner by punching or slitting in such a way that, on the one hand, the punching slits 102 and, on the other hand, the depressions 106 are formed with the dimensions already specified above.

In the present case, the term “punching” is used to describe a method in which a punching, cutting or slitting tool penetrates the flat material in order to produce the punching slots 102 there. When punching, the edge of the punching slots can be trimmed in order to thus produce the depressions 106 in one operation. The term “punching slot” is therefore not intended to be limited to slots which were produced using classic punching, but should also include slots which were produced by cutting or slitting.

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

The punching slots 102 are preferably arranged offset from one another, as shown in the various figures. They can be arranged on a “gap”, as can be seen in FIG. 5B, but they can also partially overlap one another, as shown in FIG. 8.

CH 714 025 A1 In order to make the ventilation element 100 visually appealing, it should be adapted in color. Conventional painting processes and paints are not suitable because there is a risk of clogging the punching slots and thus severely impairing the ventilation effect. The ventilation element 100 is therefore preferably coated with fine-layer powder in order to prevent clogging.

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

The two embodiments of FIGS. 1A and 2 essentially differ from one another only in the shape of the ventilation elements 100. All other elements can be identical or similar. The air supply takes place here through an air supply duct 21 with at least one air nozzle 22 pointing in the direction of the rear 101 of the ventilation element 100. These elements of the air supply are arranged in such a way that an air flow through the air supply duct 21 and from there through the air nozzle (s) 22 into the Abströmkasten 20 can flow.

The two embodiments of FIGS. 3 and 4 essentially differ from one another only in the shape of the ventilation elements 100. 3 and 4, embodiments are shown in which the air supply is constructed somewhat differently. The air supply here comprises an inflow box 23 with an air duct 25 and with at least one air nozzle 24. These elements of the air supply are arranged such that an air flow through the air duct 25 e.g. can flow laterally into the inflow box 23 and from there through the air nozzle (s) 24 into the outflow box 20. In the outflow box 20, these two embodiments behave similarly to the embodiments of FIGS. 1A and 2. In addition to the advantages already mentioned, the embodiments shown also have the advantage that they offer very good acoustic damping. The good acoustic damping results from the self-absorbing effect of the flat ventilation element 100 with punched slots 102.

Characterized in that the ventilation devices 10 according to the invention by the use of the flat ventilation elements 100 provide better performance (air introduction with larger sub-temperatures) (based on the square meter of the flat ventilation elements 100), significantly smaller-area ventilation outflow surfaces can be built in a room 1 but still produce the same cooling effect as ventilation systems with a larger ventilation outflow area or conventional air inlets with air outlets. If a conventional ventilation system e.g. with a maximum under-temperature of 8K draft-free (according to SIA 382/1), a ventilation device with corresponding slitting of the ventilation element can already introduce about twice the power (under-temperature 16 K) draft-free into the room.

[0040] Such ventilation devices 10 can be used in the ceiling, wall and floor area of a room 1.

The flat ventilation elements 100 can be used as an element of a cooling ceiling with activation, i.e. with water cooling, or as an element of a ventilation device 10, as described, use.

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

In large-scale investigations, it has been found completely surprisingly that, when appropriately finely slotted ventilation elements are used, a higher output is not necessarily related to a larger active surface, but a higher and nonetheless a compliance with certain boundary conditions when the active surface is reduced draft-free air supply can take place. This is achieved by arranging at least one active and at least one inactive surface on the ventilation element in a defined geometric ratio, which means that the surface load and temperature difference (ΔΤ) can be significantly higher without generating disruptive drafts. It seems to be important here that the active surfaces (Oa) are not too large with respect to at least one characteristic dimension, for example with respect to the width of an active surface area extending over the length of the ventilation element, so that there is sufficient room air from the sides to the active surface can flow. Only with such an arrangement, especially in the case of larger areas, by alternating active and inactive surface areas, can an effect called "spraying" be achieved which occurs when the pressure difference between the outlet box and the room to be ventilated is at least 17 to 20 Pa is. It was found that a necessary overpressure can only be easily adjusted with such a discharge box due to the narrow slots and the outlet area (s) or inactive areas of the ventilation element limited by additional inactive areas, and it can be easily adjusted by the interaction of the overpressure Arrangement of the active and inactive areas as well as the slit grid on the active areas, on the side of the ventilation element facing the room for an immediate and complete separation of the flow straight into the room, which is referred to here as spraying. Due to the geometry, the supply air flow dissolves essentially perpendicular to the surface of the ventilation element and creates a high induction effect by entraining the room air flowing in laterally. In doing so, high throwing distances can be achieved and at the same time, presumably due to the small-scale change of jet-like supply air flowing out of the slots at high speed and flowing therebetween

CH 714 025 A1 transmitter, swirled room air, drafts are avoided. For practical reasons and in order to avoid the drafts that still occur when the pressure difference is too high, the limits mentioned below, between 100 and 150 Pa pressure difference, should not be exceeded.

In order to achieve this, a ventilation device is used which, in the assembled state, has a flat ventilation element with air passage openings facing in the spatial direction, an outflow box being provided on an opposite side of the ventilation element with an air supply for supplying an air flow and the ventilation element in known manner has a plurality of slots made in a grid comprising rows and columns 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 grid (Z1), i.e. the distance between the non-offset lines is 1 mm to 15 mm. In this case, between two lines that are not offset with respect to the x direction, a line offset with respect to the slot positions in the direction of the x axis can be inserted approximately half the distance (Z1 / 2). The offset can be of the order of about 1 to 2 slot lengths. The slot lengths and slot widths of the staggered lines are also in the ranges specified above, but the dimensions of the slots in the unstaggered lines can be different or the same. The column grid (S1), i.e. the distance between the columns, in particular between the columns of the same row height, is 0.5 x L to 2 x L, i.e. 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.

According to the invention, the ventilation element comprises at least one active surface area O _A and at least one inactive surface area O | and for at least one characteristic dimension x _A , for example the length, width, height, diameter etc., of the active surface area O _A :

L xa L 50 L, preferred

L <xj <35 L.

Active surface area O _A is understood here to mean a ventilation-active surface area, that is to say a surface with a grid as mentioned above, in which air can flow through the slot grid, while inactive surface areas O | the slot grid is either covered or not provided from the outset. Similar or even the same dimensions of a characteristic dimension X | can be set:

L S xi i 50 L, d preferred

L <Xi <35 L.

[0047] For the characteristic dimensions of the active surface area O _A and the inactive surface area O | 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 |) <1000 mm, preferably 8 mm <(O _A or Oi) <350 mm.

The grid should include 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 a corresponding width.

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

The surface of the ventilation element can be flat, cylindrical or prismatic. Cylindrical and prismatic are also understood here to mean only partially cylindrical or partially prismatic surfaces, such as those used for the use of so-called corner sources, i.e. For example, quarter-cylindrical ventilation devices that are used in a corner of the room are used. With regard to the prismatic shapes, reference is made here in particular to advantageous designs with regular hexagons or octagons or their half or quarter prismatic embodiments.

[0051] The surface of the ventilation element can comprise alternately arranged active surface areas (O _A ) and inactive surface areas (Q). Examples of this are strip-shaped, wavy or checkerboard-like arrangements. Alternatively, several active surface areas (O _A ) or several inactive surface areas (O |) can be distributed in an inactive or active field on the surface of the ventilation element. For example. active or inactive surface areas arranged as circles, ellipses, triangles, quadrilaterals or other polygons, for example rectangles or rhombohedra, in an inactive or active field.

The ratio of the active surface area (O _A ) to the inactive surface area (O |) can be as follows:

CH 714 025 A1

0.2 <O _a / Oi <0.6, preferred here

0.2 5 <Oa / Οι <0.55 [0053] The device can be at least partially or as a whole cylindrical or prismatic, with cylindrical or prismatic active surface areas (O _A ) of the ventilation element (O _A ) of one another in one direction of a cylinder or prism axis. 100) alternate with cylindrical or prism-shaped inactive surface areas, the height h _{A being} the characteristic size of the active surface area and the height h | is the characteristic size of the inactive surface area. This version is suitable, for example, for columnar, standing 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 cylindrical or prism-shaped surface areas, these are also referred to below as rings or as rings.

Alternatively, an at least partially or wholly cylindrical or prismatic device can have at least one cylinder segment or at least one prism segment of the surface of the ventilation element, a continuous or only at greater intervals interrupted active and / or a corresponding inactive surface area (O _A , 0 ) exhibit. With larger diameters, several alternating active and inactive surface areas can advantageously be arranged along the circumference, parallel to the cylinder or prism axis.

The slit grid can be formed essentially over the entire surface of the ventilation element, whereby, as is known to the person skilled in the art, marginal areas are excluded, for example for processing reasons, and the inactive surface areas (O |) of the ventilation element are formed by flat covers can.

The cover can be formed by a sheet of film or a paint covering the slots and basically be attached to the inside or the room side of the ventilation element facing the room. The sheet or film can be glued or, in particular, can only be clamped on the inside when it is attached. For example, the cover can comprise an elastic, completely or partially cylindrical or completely or partially prismatic curved film or sheet which is clamped or / and glued to the ventilation element in the device, for example, which is at least partially cylindrical or partially prismatic.

Basically, in all forms of training, the ventilation element can comprise a metal plate with a thickness (D) between 0.5 and 2 mm or be produced as a whole from such. The material can be, for example, a sheet, for example made of electrolytically galvanized (EVZ), stainless steel or aluminum. The slots can be introduced into the material as mentioned above, wherein a ratio (V) of the punch slot circumference (U) to the punch slot area (F) can be, for example, between 2.7 and 22. The free cross-section (FQ) per unit area of the active area O _{A of} the ventilation element can be in the range from 1 to 20%, preferably in the range from 2 to 10%. Furthermore, each punching 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 at half a row spacing Z1 / 2. The slots of the further line can be offset with respect to the x-axis, preferably symmetrically offset with respect to the slots of the two immediately adjacent lines. The slots of the rows and the slots of the other rows can form an overlapping, flush or spaced 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 lines.

The air supply of the ventilation device can comprise an air supply duct with at least one air nozzle pointing in the direction of the rear of the ventilation element, these elements of the air supply being arranged such that an air flow through the air supply duct and from there through the at least one air nozzle into the outflow box can flow.

Alternatively, the ventilation device can also comprise an inflow box as described above with an air duct and at least one air nozzle, these elements of the air supply being arranged such that an air flow through the air duct into the inflow box and from there through the at least one air nozzle into the outflow box can flow. Inflow box and / or outflow box can also be cylindrical or prismatic in the case of cylindrical or prismatic ventilation devices. For example. A cylindrical or prismatic outflow box with a larger diameter / circumference can contain a cylindrical or prismatic inflow box with a smaller diameter / circumference.

The present invention also includes a ventilation device with a plurality of ventilation devices as described above.

CH 714 025 A1 Furthermore, the present invention also includes 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 from 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 of the outflow box facing the inside and the outside of the flat ventilation element facing the room, the pressure difference being in a range from 17 to 150 Pa, preferably from 20 to 100 Pa is set.

The induction number, i.e. the ratio of the entrained amount of secondary air to the introduced amount of primary air in the near field, for example at a distance of 800 mm from the surface, in particular from a central area of an active surface of the ventilation unit, can be set from 5 to 20, preferably from 10 to 15, which corresponds to a very high value. To determine the induction number, 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.

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

It should be expressly pointed out here that the invention includes all combinations of individual features which are also not expressly mentioned in examples and which are only disclosed in connection with another exemplary embodiment, as long as such a combination would not be recognized by the person skilled in the art from the outset as meaningless , Likewise, the invention also relates to corresponding combinations of a feature according to the invention with a feature adopted from CH 702748 as prior art.

The present invention is described below on the basis of various exemplary embodiments with reference to FIGS. 9 to 12 and tables 2 and 3. Show:

Figure 9A is a schematic sectional view of a tubular ventilation device of the prior art; Figures 9B and 9C each a schematic sectional view of a tubular ventilation device according to the invention; Figure 10A a schematic view of a columnar ventilation device of the prior art; Figure 10B a schematic view of a columnar ventilation device according to the invention; 11A to 11C Various schematic embodiments of a flat ventilation element for a ventilation device; Fig. 12 a schematic embodiment of a tubular ventilation device with a cylindrical segment 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 cylindrical segment and a plurality of annular inactive surfaces; Fig. 15-19 Different versions of column-shaped ventilation devices with ring-shaped or cylindrical active or inactive surfaces;

Fig. 9A schematically shows the flow pattern, ascertained in a cloud chamber, of a tubular ventilation device 10 of the prior art, mounted under a ceiling, in which essentially, i.e. apart from the cover by clips and nozzles, the entire cylindrical surface as the active surface Oa with a slot grid as described above 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 rows aligned in columns, as in all experiments, analogously to FIGS. 5A, B, a further row of slots of the same geometry was arranged flush with one column. The slot grid was oriented transversely to the direction of flow with respect to the longitudinal axis (3 mm) of the slots. The slot openings were slightly inclined with respect to the surface of the ventilation element (depth direction, for example perpendicular to the sheet plane of the drawing 5A, 5B)) against the main axial flow direction of the tube.

CH 714 025 A1 The experiments were carried out in a large-scale laboratory with a room height of 3350 mm and a base area of 4200 x 6500 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 on the ceiling at a hanging height H (ie distance from the pipe center to the ceiling). The room temperature was set at approx. 26 ° C, the supply air was approx. 5 K lower. The supply air flow was regulated with an iris diaphragm (nominal width 125 mm) at the supply air inlet of the pipe. The iris diaphragm is fully open in position 1. The corresponding volume flow V'zul adjusts itself as a function of the temperatures of the supply air and room air and the exhaust air volume V ' _ABL , which is not dealt with here. Further details on the tests carried out with the pipe suspended horizontally under the ceiling can be found in Table 2, and with regard to the geometrical arrangement of the free and hidden surfaces, FIGS. 9B and 9C, or for tests 20 and 21 in FIGS be removed. The further details given in the table relate to the following information: the test number; the suspension height; each from the ceiling to the center of the pipe / axis, measured in millimeters; the covered area, in this case taped (area in m ² ); the additional area covered by brackets or sockets; the free area; the corresponding area load in m ³ / (h * m ² ), which results from the volume flow V '(in m ³ / h) of the supply air that is also given; the setting of the iris; the supply air T _ZUL and the room temperature T _room in ° C; the differential temperature ΔΤ between the room and the supply air in K; the pressure difference A _PS t between the overpressure inside the tube and in the room; the measuring heights for measuring the air speed in the room in cm from the floor level of the test room; and the corresponding air velocities v _L runs in mm / s (average over 180 seconds).

It turned out that, in the case of a tube 10 with an essentially completely active cylindrical surface, initially, as sketched in FIG. 9A, an essentially vertically downward flow L6 is formed, which is distributed laterally only in the bottom region , which can lead to noticeable drafts both under the ventilation and in the floor area. With a measuring tree set up below the pipe 10 at a distance from the pipe axis, velocities between 185 and 300 mm / s were measured at a height of 180 cm. The distance was set in such a way that the measuring tree was located in an area of the greatest cold air drop (highest flow velocity) previously determined by flue gas tests. Experiments with the numbers 1,2, 6, 7 and 9 refer to such an experimental arrangement.

Alternatively, in experiments 3, 4, 5, 8, 10, 11, 12 and 13 the lower half of the cylinder was taped with a film, analogous to FIG. 9B, in accordance with the information in the table. As a characteristic or characteristic variable for the active or inactive surface area, O _A or O | the respective circular arc k _A , k | be considered. The flow pattern in tests 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), surprisingly, a very different flow behavior of the supply air flow L7 or L7 'as shown in Figures 9B and 9C. The air flow is sprayed from the slots not shown here, as from nozzles under the ceiling or laterally into the room. The room air is entrained by the supply air, as indicated by arrows L8 and L8 '. This mixture of supply air and indoor air then drops over a large area at a relatively low speed. If the test arrangement is otherwise the same, the flow speed becomes clear at a height of 180 cm, for example from 210 to 140 mm / s (compare 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 reduced (compare experiments 11, 12, 13, to experiment with an arrangement according to the prior art in experiment 9).

In experiments 11 and 12, as shown in FIG. 9C, the upper semi-cylindrical active surface area was divided by an additional cover 11 arranged therebetween, which gives the characteristic size k _A 'for the active surface and the characteristic size for the inactive surface characteristic sizes k | and k / result. A throw of one meter was achieved for trial 11. With the same geometry and significantly increased pressure or surface load as shown in experiment 12, the range could be doubled to 2 m, but too high an air velocity and thus drafts occurred at all measuring heights. In contrast, experiment 13 shows a very favorable setting of the pressure difference for an arrangement identical to experiment 10, ie covering the lower cylinder segment. A throwing distance of 1.3 m was achieved without any drafts. The throwing height from the pipe axis was 0.6m in experiments 12 and 13. This size corresponds to the height component of the throwing distance measured from the pipe axis.

In experiment 20, instead of covering one or more circular segments of a tube with the same dimensions as in the previous experiments, a multiplicity of substantially ring-shaped inactive surfaces was produced by masking the surface of ventilation element 100. As shown in FIG. 13, a total of 44 free rings, each 20 mm wide, of active surface were left free, which are separated by strips of inactive surface area, inactive surfaces of ventilation element 100 become black, active white here and in FIGS. 14 to 19 shown. The latter partly have a different ring thickness as shown, see Fig. 13. Surprisingly, it turns out that such an arrangement can be operated with an unusually high pre-pressure and surface load, only slightly exceeding the limit specified normatively for draft in the ground-level measuring range of 150 mm / s was measured. The air temperature at the three measuring points was much closer to the room air, which suggests a very high induction. It should be remembered here that the measuring points were set up at the locations with the highest flow speeds, see above.

CH 714 025 A1 Similar to experiment 20, as shown in FIG. 14, the arrangement for experiment 21 is also that, in this case, a tube segment with an arc of 140 mm in length is additionally in the lowest region of the tube is covered in a symmetrical area with respect to the suspension. With such an arrangement, the ventilation device could be operated with an even higher surface load and thus a higher pressure difference, and without the normatively permissible air speed being exceeded in any area of the room.

10A shows the schematic flow diagram of a columnar, vertical ventilation device 10 of the prior art, determined in a cloud chamber, in which the majority of the cylindrical surface is designed as an active surface Oa with a slot grid as described above. A tree-shaped flow pattern L4, which develops symmetrically around the device, can be clearly seen. Details of such an experiment with a 2 m high column with a 200 mm diameter can be found in Table 3, Experiment 16, the geometric arrangement from FIG. 16. The ventilation arrangement 10 consists of a base plate 26, a 150 mm high base 27, the columnar ventilation element 100 placed thereon and the air supply not shown here. The flow velocity at a distance of half a meter from the pipe, measured at a height of 130 and 180 cm, is very low at 30 mm / s, see column «Air speed in the room», and therefore the ventilation is poor. Due to the relatively rapid drop in the supply air, which is much cooler here because the air is poorly mixed, a draft behavior perceived as uncomfortable near the floor can develop even with relatively low ventilation performance, despite the fact that the ventilation effect in the rest of the room is very low.

In contrast, 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 Oa, Oi are arranged in an alternating sequence in a ring. Due to the increased pressure inside the device due to the partial covering of the cylindrical surface, the nozzle effect of the slot grid is significantly increased under otherwise identical test conditions, which, in combination with the corresponding geometric dimensions, in particular of the active surface areas O _A , increases the supply air flow L5 completely and essentially perpendicular to the active cylinder surface Oa and at the same time entrains room air in the form of a vortex flow L6 from the adjacent areas. The characteristic dimensions in this case are the heights of the cylinders with active and inactive surfaces tu and h | be considered. In experiments 14 and 15, with a column 2 m high, tu and h | each 120 mm. Geometric details are shown in FIG. 15. In experiment 15, in which a similar surface load was set as in experiment 20, the behavior and pressure difference are similarly favorable. The results are also appealing with the lower surface load of test 14, even if the cooling capacity is lower.

17 to 19 whose results are described in the corresponding experiments 17 to 19 in Table 3. Here, too, two-meter-long pipes with a diameter of 200 mm and an identical slot grid were used as ventilation elements and the corresponding area ratios and geometries were produced by masking the slot grid with film. With the exception of the suspension height not used here, Table 3 contains the details of the same settings and parameters as described in detail in Table 2.

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

In contrast, the results of experiment 17 with a columnar ventilation element with a continuous active surface in the upper half and a continuously inactive surface in the lower half, as shown in FIG. 17, are less satisfactory. In particular, the permissible air speed is exceeded, albeit slightly, in the lower area.

On the other hand, as shown in FIGS. 18 and 19, configurations of the ventilation element in which only the lower or only the upper half of the surface is provided with ring-shaped active surface areas, while the other half of the surface is inactive, offer the possibility to operate the ventilation device 10 with a very high surface load and thus a high pressure difference, which favors the vertical expansion of the supply air from the surface of the ventilation element into the room, in particular with a slot grid arranged transversely to the supply air flow in the pipe. This phenomenon applies to all ventilation devices or methods according to the invention, as well as fundamentally all the features shown in connection with an embodiment or on the basis of an embodiment can also be combined with other embodiments or examples, provided that this is not obviously contradictory for the person skilled in the art.

Furthermore, in general with conventional pipe dimensions, the provision of an inflow box is superfluous, rather it is sufficient here, depending on the pipe length, to provide the power supply from one side or, for example, in a T-shape from the center, so that an axis-parallel main flow occurs in the The interior of the tube adjusts from which the partial flows carried away by the slot pattern branch off laterally, the tube simultaneously forming the outflow box. Alternatively, especially in the case of large diameters, an inflow box arranged, for example, along the tube axis or in the region of a segment with an inactive surface can also be provided.

CH 714 025 A1 It should be noted that comparable favorable behavior could never be achieved with a continuously active surface even if higher pressure differences and / or surface loads were set (see, for example, experiment 16). Obviously, the correct setting of the ratio of the active to the inactive area and the arrangement geometry, i.e. the arrangement of the active and inactive areas, particularly in the case of large-area ventilation devices, contributes significantly 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, the cylindrical ventilation element 100 a w.o. has described slot grid with slots aligned parallel to the cylinder axis. The difference in flow behavior with otherwise identical test parameters thus only resulted from the different covering / arrangement of the active or inactive surfaces, which here was only for practical reasons by externally masking different surface areas with adhesive film.

In general, it can be noted that in any tubular ventilation device, the use of a ventilation element (100) which has a plurality of alternately arranged ring-shaped or partially ring-shaped active and inactive surface areas has proven to be advantageous in operation. This allows a larger pressure difference to be built up between the inside of the pipe and the surroundings, which enables the occurrence of a spray effect with increased throw distance and induction and, in addition, a greater cooling / heating capacity. This applies not only to circular, cylindrical or polyhedral pipe cross sections, but also to corresponding half or quarter pipe cross sections, such as those used for ventilation devices that can be operated on a wall or a corner of the room.

Further examples of the division of surfaces, in particular for large-area ventilation devices with a total area, for example, larger than 1 or 2 m ² , are shown in FIGS. 11A to 11C.

11C shows an arrangement of circular active surface area O _A in an inactive field O | a flat ventilation element 100, which can be shaped in one plane or, for example, also as a quarter, half or full cylinder. The diameter d _A can be regarded as the characteristic dimension of the active surface area O _A. The characteristic size of the inactive surface is the unspecified diameter (double arrow) of the dashed circle inserted between the active surfaces. It should be noted that the specification of a characteristic size or dimension X | can only be advantageous for the inactive surface area if the area of the ventilation element in the direction of both surface coordinates is larger than the characteristic size or dimension x _{A of} the active surface area. In particular, it is larger than twice the dimension x _{A of} the active surface area.

11B shows a corresponding ventilation element 100 with alternating strip-like arranged active and inactive surface areas O _A and O | with corresponding characteristic dimensions b _A , b |. 11C shows a checkerboard-like arrangement, but in which the inactive surface areas O | are continuous in two directions and form intersecting, here orthogonal, corridors through which the ambient air can flow particularly easily in the direction of the active surface areas O _A. As a result, the induction effect can be further improved, especially in the case of large-area ventilation elements 100. Characteristic dimensions here are the side length (n) Sa of the active area O _A and the corridor width (n) si of the inactive areas O |. Of course, such an effect can also be combined with corridors which run obliquely with respect to one another and / or with active surface regions which are in particular elliptical and circular.

12 shows a further tubular ventilation device 10 according to the invention in which the inactive surface areas O | of the ventilation element 100 are continuous in two stripes 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> 3 K), in particular in the case of a corresponding undertemperature of the supply air and greater cooling capacity. In the lower area of the pipe, the slot grids are covered or not implemented, which results in a more favorable distribution of the supply air, in particular a supply air with a lower temperature than the room air. Analogously, such tubes can also be designed as vertically standing columns, the inactive surface parallel to the tube axis, depending on the installation location, for example, being able to be arranged in several narrower strips distributed over the circumference.

In general, it is advantageous in the case of pipes, because of a higher dynamic pressure which is formed in the pipe interior by the volume flow, to design the slot patterns in such a way that they are transverse, in particular perpendicular to the flow direction, since this causes a rapid separation of the flow from the pipe surface into the pipe Into space, for example substantially perpendicular to the outer surface of the ventilation element 100 facing the space, is facilitated. The slots can also be inclined with respect to the surface of the ventilation element either vertically or, as is often unavoidable for manufacturing reasons, slightly in (ie angle slightly less than 90 degrees) or counter (ie angle slightly larger than 90 degrees) the axially directed main flow direction ( for example in a range from 0 to 10 degrees, ie for example 80 to 110 degrees with respect to the surface).

The orientation of the slot rater generally plays a minor role in box-shaped ventilation devices, in particular if they additionally have an inflow box 23, which already redirects the air flow from an orientation parallel to the pipe axis in the direction of the inner surface of the ventilation element. On the other hand, it can be in the case of tubular or columnar ventilation elements, or in general, essentially parallel to the inner upper

CH 714 025 A1 surface of the ventilation element guided supply air flow and parallel alignment of the longitudinal axis of the slots lead to an undesirable flat or even surface parallel exit of the supply air into the room, which makes it difficult for the air flow to become detached and the ventilation performance to deteriorate noticeably. In particular, this causes a smaller throw range and less induction.

In the case of exclusively downward flows, it has proven to be advantageous to provide more and / or greater distances between the active surface areas, ie to increase the proportion of the inactive surface. For example, if the active and inactive surfaces of a cooling ceiling are arranged in strips, the characteristic dimension x _h in this case can be the width bi of the strips of the inactive surface O | 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 from 8 to 350 mm. In addition, the active areas can be interrupted by inactive areas, for example as detailed above.

CH 714 025 A1

Table <M

8 o 2 0 I- 1 1 1 1 CO 3 E > E 200 160 100 185 180 100 115 115 100 140 140 115 145 140 85 220 160 160 VLUFT measuring height cm 180 130 10 180 130 10 180 130 10 180 130 10 180 130 10 180 130 10 cl <i 1 1 LT) 11 1 1 <5 5 5:50 5:00 5:00 5:50 4.80 5:00 J o ^U t 20:40 20.95 21:00 20:50 21:20 21:00 e _o ^u κ ° H 25.90 25.95 26.00 26.00 26.00 26.00 m > E 132 132 132 132 228 228 cover 125mm (N C \ l Wing load m ³ / h * m ² 120.1 120.1 240.2 240.2 414.9 207.5 Free area Oa m ² 1099 1099 0.5495 0.5495 0.5495 1099 Additional dil. Oi m ² 00:16 00:16 80Ό 00 o Ó CO o Ó 00:16 Abgekl. Area oi m ² O O 0628 0628 0628 O Suspension height Pipe axis mm 150 150 150 150 150 150 Vers.Nr. rh r \ i CO "3- LT) <0

CH 714 025 A1

Table 2 - continued

«<_> S 0 H 1 1 VLUFT mm / s 210 210 160 140 110 110 300 300 125 100 100 170 110 140 06 200 160 180 VLUFT measuring height cm 180 130 10 180 130 10 180 130 10 180 130 10 180 130 10 180 130 10 è- LA 20 • 17 32 ΔΤ Supply air space K 5.85 5:40 5:40 5.70 5:50 5:40 j o ° 1 1 20:15 20.70 20.80 20:50 20:50 20:50 f o or ο Η 26.00 26.10 26.20 26.20 26.00 25.90 τ · 4 m > Ξ 300 300 300 300 275 LH σι m cover 125mm per cent per cent v-1 per cent per cent per cent Wing load m ³ / h * m ² 273.0 546.0 273.0 546.0 1------------------------------------------------- -------------------------------------------------- -------------------------------------------------- ------------------------------------------------- 594.0 853.1 Free area Oa m ² 1099 0.5495 1099 0.5495 0463 0463 Additional dil. Oi m ² 00:16 80Ό 00:16 00 O b 00:07 00:07 Abgekl. Area 0, m ² O 0628 O 0628 0728 0728 Suspension height Pipe axis mm 150 150 950 950 950 ¹ 950 Vers.Nr. 00 cn 10 11 12

CH 714 025 A1

Osi tn a p N -P Φ CO -U P O fa

I

CX1

Φ <—I Ή

Φ X)

H3 H

a ο .> o I- 25.10 25.25 24.70 25.25 25.40 25.10 en t> ³ 1 140 110 120 145 110 165 130 06 120 measuring height VLUFT cm 180 130 10 180 130 10 180 130 10 - p 26 40 09 ΔΤ Supply air space K 5:50 5:50 5:40 s <_) h? ° 26.40 25.60 20:40 20:50 20:40 E «l · ² H 25.90 26.00 25.80 Ξ> <fxl <r> > E 395 460 450 cover 125mm per cent v-i per cent Wing load m ³ / h * m ² 718.8 836.4 1046.5 Free area Oa m ² 0.5495 00:55 00:43 Additional dil. Oi m ² 00 ο ό 00Ό 00Ό Abgekl. Area O | m ² 0628 0.71 0.83 Suspension height Pipe axis mm 950 950 950 Vers.Nr. 13 20 21

CH 714 025 A1

Table 3: Experiments with column-shaped ventilation devices; the measuring tree was set up half a meter from the pipe;

1 o H 25.40 25.10 24.00 25.30 25.10 23.80 25.50 25.15 22.90 26.20 25.50 24.15 25.90 25.20 24.55 26.20 26.00 24.40 (Λ 2 'S > E 50 50 100 50 40 o CM vH 30 30 110 30 110 155 45 125 125 25 35 06 VLUFT measuring height cm 180 130 10 O 00% 130 10 180 130 10 180 130 10 180 130 10 180 130 10 g £ 25 37 16 40 O 00 80 ΔΤ Supply air space K 5.20 5.15 5.20 5:50 5.20 5:40 1 - 26.30 26.30 26.50 20.60 20.70 20.60 20:50 20.60 20.60 e QÎ ° 1- 25.80 25.85 25.80 26.00 25.80 26.00 <m > E 395 490 490 460 460 460 m > E 395 490 490 460 430 430 cover D = 125 mm per cent per cent per cent per cent per cent Wing load m ³ / h * m ² 651.8 00 o 00 423.9 798.6 1242.8 1242.8 Free area 0a m ² 909Ό 0606 1156 0576 0346 0346 Additional dil. Oi m ² 00:00 00:00 o vH Ó 00:05 00:05 00:05 Abgekl. Area oi m ² 0.65 0.65 O 0.63 0.86 0.86 Vers.Nr. 14 15 16 17 18 19

CH 714 025 A1

LIST OF REFERENCE NUMBERS

[0093] breather 10 Abströmkasten 20 air supply 21 air nozzle 22 Anströmkasten 23 air nozzle 24 air duct 25 baseplate 26 base 27 flat 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 rear (main5) level e Punching slot surface F free cross section FQ total area GF Total area of all wells FV Total area that is normal GFN slot length L airflow L1, ... L8 Primary air flow L2 Induction air flow L3 Active, inactive surface Oa, Oi room R depth T1 Punching slot extent U

CH 714 025 A1

slot width

offset

LIST OF REFERENCE NUMERALS - continued [0094]

Characteristic sizes of the active, inactive surface (s) x _A , Xi

Characteristic. Height active / inactive

Characteristic. Circular arcs active / inactive h _A , h.

k _A , k.

Claims (26)

claims 1. Ventilation device (10) for mounting in a room (1), the ventilation device (10) in the assembled state having a flat ventilation element (100) facing in the direction of the room with air passage openings, and an outlet box (20) on a rear side opposite the room direction ( 101) of 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 grids comprising rows (109) and columns (110) Has attached slots (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, the line grid (Z1) 1 mm up to 15 mm and the column grid (S1) is 0.5 x L to 2 x L, characterized in that the ventilation element (100) comprises at least one active surface area (O _A ) and at least one inactive surface area (Oi) u nd for at least one characteristic dimension x _{A of} the active surface area (O _A ): 3 L <x _A <50 L. 2. Ventilation device (10) according to claim 1, characterized in that for at least one characteristic dimension X | of the at least one inactive surface area applies: 3 L <X | <50 L. 3. Ventilation device (10) according to one of the preceding claims, characterized in that the grid comprises at least three rows and three columns. 4. Ventilation device (10) according to one of the preceding claims, characterized in that the surface of the ventilation element is flat, cylindrical or prismatic. 5. Ventilation device (10) according to one of the preceding claims, characterized in that the device comprises a plurality of active surface areas (O _A ) and / or a plurality of inactive surface areas (O |) distributed on the surface of the ventilation element (100). 6. Ventilation device (10) according to claim 5, characterized in that the surface of the ventilation element (100) comprises alternately arranged active surface areas (O _A ) and inactive surface area (Oi). 7. Ventilation device (10) according to one of the preceding claims, characterized in that the following applies to the ratio of the active surface area or the active surface areas (O _A ) to the inactive surface area (Oi) or to the inactive surface areas: 0.2 <O _A / Oi <0.6. 8. Ventilation device (10) according to one of the preceding claims, characterized in that the device is cylindrical or prismatic, at least one cylinder segment or at least one prism segment of the surface of the ventilation element (100) having an active surface area (O _A ). 9. Ventilation device (10) according to one of claims 1 to 6, characterized in that the device is cylindrical or prismatic, with each other in a direction of a cylinder or prism axis cylindrical or prism-shaped active surface areas (O _A ) of the ventilation element (100) alternate with cylindrical or prism-shaped inactive surface areas, the height h _{A being} the characteristic size of the active surface area and the height hi being the characteristic size of the inactive surface area. 10. Ventilation device (10) according to claim 8, characterized in that the height of the cylindrical or prism-shaped active surface area is 60 to 180 mm. 11. 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 or the inactive surface areas (Oi) of the ventilation element (100) formed by flat covers are. 12. Ventilation device (10) according to claim 10, characterized in that the cover comprises a sheet of film or a coating covering the slots. CH 714 025 A1 13. Ventilation device (10) according to any one of claims 7 to 11, characterized in that the cover comprises an elastic completely or partially cylindrical or completely or partially prismatic curved film or sheet, which in the cylindrical or prismatic device (10) the ventilation element (100) is clamped and / or glued. 14. Ventilation device (10) according to any 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). 15. Ventilation device (10) according to one of the preceding claims, characterized in that each punching slot (102) has a ratio (V) of punching slot circumference (U) to punching slot area (F) which is between 2.7 and 22. 16. Ventilation device (10) according to any one of the preceding claims, characterized in that at least one further row of slots (102 ') is arranged between the rows of the grid at a distance Z1 / 2. 17. Ventilation device (10) according to claim 16, characterized in that the slots (102 ') of the further row are offset with respect to the x-axis, preferably symmetrically offset with respect to the slots (102) of the two adjacent rows. 18. Ventilation device (10) according to claim 16 or 17, characterized in that the slots (102) of the rows and the slots (102 ') of the further rows form an overlapping, flush or spaced arrangement of columns. 19. Ventilation device (10) according to one of claims 16 to 18, characterized in that the slots (102 ') of the further line each have a slot length (L) between 2 and 10 mm and a slot width (W) between 0.1 and 0 , 8 mm. 20. Ventilation device (10) according to 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. 21. Ventilation device (10) according to 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%. 22. Ventilation device according to one of the preceding claims, characterized in that the ventilation element (100) has a plurality of alternately arranged annular or partially annular active and inactive surface areas. 23. Ventilation device with a plurality of ventilation devices (10) according to one of claims 1 to 17. 24. The method for operating a ventilation device (10) according to any one of claims 1 to 22, characterized in that the device is operated with an air throughput of 100 to 2 ^Λ 000 m ³ / h per square meter of active area. 25. The method according to claim 24, characterized in that the device is operated with a pressure difference between the inside and outside of the flat ventilation element of 17 to 150 Pa. 26. The method according to any one of claims 24 or 25, characterized in that the device is operated with an induction number of 5 to 20. CH 714 025 A1 1 Fig. IA