EP0681674B1 - Ventilation device - Google Patents

Abstract

PCT No. PCT/EP94/00256 Sec. 371 Date Jul. 27, 1995 Sec. 102(e) Date Jul. 27, 1995 PCT Filed Jan. 29, 1994 PCT Pub. No. WO94/18506 PCT Pub. Date Aug. 18, 1994The invention relates to a ventilation device. Provision is made that the air propulsion plant (20) conveys at least a portion of the air in an air circulating mode by means of at least one variable volume chamber (6) in a pulsating manner at a very low frequency, with the chamber being connected to the room (2) by at least one air passage (21).

Description

The invention relates to a ventilation device according to the preamble of claim 1 (see e.g. WO-A-9218814 and JP-A-03 249 383).

There is an increasing need for ventilation equipment. This is especially true when it comes to compact facilities. They are preferably used for the thermodynamic treatment of the room air of one or more room axes, in particular a single room or a room zone of this room / single room. Such devices are preferably used in office buildings and hotels. The advantage of such devices lies in the simple retrofitting of the rooms, since in the case of air treatment, for example for a heating or cooling process, only an electrical power and a water connection are required, provided that there is a pure recirculation mode.

The known ventilation technology devices of the previous type have a fan that draws in air from the room and feeds it, for example, to a heat exchanger. The air heated or cooled by means of the heat exchanger is then returned to the room due to the conveying effect of the fan. The relatively high noise level of the fan is disadvantageous. Engine noise can Although they are largely steamed when the motor is not in the air flow, for example in compact drum rotors and axial fans with external rotor motors, the motor noises are inevitably emitted as airborne sound. The share of motor noise in the overall noise of the fan can therefore only be reduced by choosing a relatively quiet and low-vibration motor. Flow noises are always present at the fan blades. They can only be reduced by lowering the speed. However, this leads to an oversized fan. As a result, the frequency spectrum shifts to a lower frequency range, as a result of which the weighted sum level decreases slightly. However, the efficiency of the motor drops because it is operated far outside its design range. As a result of the necessary oversized power of the engine, the size, price and heat emission also increase. In this way, there are narrow limits to noise reduction.

Another way to reduce airborne noise is to use silencers on the suction and pressure side of fans. However, this excludes inexpensive, compact devices for one or more spatial axes.

The invention is therefore based on the object of providing a ventilation device of the type mentioned at the outset which is of simple construction, works reliably, is inexpensive and in particular works quietly. In particular, a long lifespan of 10,000-20,000 operating hours should also be achieved.

This object is solved by the features of claim 1. As a result, at least a portion of the conveying air is sucked out of the room by increasing the volume of the chamber and moved back into the room by reducing the volume of the chamber. When sucking in and / or moving back, the air passes through the airway. Surprisingly, it has been shown that sucking in and expelling air does not lead to a "short circuit". No "short circuit" means that the same volume of air is not constantly sucked in and expelled again. This is possible due to the pulsating delivery of the air, since the ejection takes place with such an ejection pulse that the ejected air detaches as a vortex and penetrates into the room. New room air can then flow in during subsequent suction. If, according to a further development of the invention, the ventilation device has an air treatment device, for example a heat exchanger, then only a cooling and / or hot water connection and a power connection are required for an installation required. The ventilation system is therefore particularly suitable for retrofitting if, for example, the heat load of a room has changed. As already mentioned above, the ventilation equipment serves to act upon a room or a room zone of this room. If "space" is mentioned in the following, this can of course also be an area of this space, namely the space zone mentioned. If one speaks of "room zone", it can also be a complete room. The above statements naturally also apply to the claims.

The arrangement can be such that no air treatment device is provided, that is, the ventilation device only serves to supply the room zone or the room with conveying air, at least a portion of this conveying air being conveyed in recirculation mode, that is to say, air becomes the room zone removed (by enlarging the chamber volume) and then ejected into the room again (by reducing the chamber volume). It is possible that this process takes place exclusively, that is to say that there is pure recirculation mode. However, it is also conceivable that there is a mixed operation, that is, a part of the conveyed air is conveyed in the recirculation mode and another part in the fresh air or primary air mode, that is, this air portion is introduced into the chamber in a suitable manner and because of the chamber volume reduction in the room zone. Purely primary or fresh air operation is also conceivable. In the course of this application, this type of operation should be considered when disproportionately little air is sucked in from the room zone, ie when the supply of primary or fresh air predominates significantly.

Since the air path forms both an air intake path and an air exhaust path, one and the same air path takes over both functions. This means that there is also a compact design, i.e. a high calorific output per construction volume.

It is therefore advantageous to use the air conveyor to generate vortices when the air is expelled, which vortices have at least such a high momentum that they detach and penetrate into the room. Thus, a pulsating flow is generated by means of the air delivery system when the air is expelled, which is so energetic that, as mentioned, it separates and is therefore not sucked in again.

The change in volume of the chamber is brought about by means of a drive device which preferably operates with a selectable frequency in the range from 0.1 to 30, in particular 0.1 to 5 Hz. This low-frequency operation has proven to be particularly favorable acoustically, since it is below the hearing threshold.

According to a development of the invention, it is provided that an air treatment device - as already mentioned - is located in the airway. This air treatment device can be, for example, the already mentioned heat exchanger. However, it is also possible for a device which influences the air humidity to be used as the air treatment device. Alternatively, it is also possible to use a substance conversion device, for example a catalyst, which influences the air conveyed. This list is not exhaustive, but other known, but not mentioned, air treatment devices can also be used, whereby combinations of different air treatment devices are also possible.

If the term "heat exchanger" is used in the following (this applies both to the introduction to the description and to the description of the figures), this is not intended to be a limitation, but rather to clarify a type of possible air treatment devices. Instead of the heat exchanger mentioned, another or a combination of different air treatment devices can also be used. Furthermore, it is possible that where such a heat exchanger or an air treatment device is mentioned in the course of this application, no such device is used, that is to say that there is no air treatment device in the airway, so that the ventilation device according to the invention merely serves to promote Air or gas serves, but does not treat the air and / or the gas at the same time.

The airway is preferably kept as short as possible. In particular, it is designed only as an opening with the adjoining heat exchanger. The actual airway length is thus limited to the passage of the heat exchanger.

A piston element is preferably arranged in the chamber of the ventilation device. The volume change is brought about by displacement of the piston element.

According to one embodiment of the invention, the piston element can be designed as a translationally moved piston. Alternatively, however, it is also possible to design the piston element as a displacement element which can be pivoted about an axis in the manner of a flap. The chamber volume is increased or decreased by a pivoting movement of the displacement element. The shape of the walls of the chamber is adapted to the movement arc of the displacement element. Since the piston element is subject to considerable acceleration forces, it is preferably plate-shaped and therefore light.

To adjust the air flow rate per unit of time, the frequency of movement of the piston element and / or the stroke can be varied and can thus be set to a desired value. In addition or alternatively, it is also possible to vary the size of the swivel angle of the displacement element and thus to make it adjustable to a selectable value.

The base area of the chamber adjoining the heat exchanger can be larger than the base area of the heat exchanger. In such a case, it is advantageous that the air opening of the heat exchanger is arranged offset with respect to the larger, adjacent base area of the chamber in the direction of the pivot axis of the displacement element. With such a design, a particularly favorable vortex detachment of the expelled air takes place.

If the displacement element is in its movement reversal position at the end of the ejection phase immediately adjacent to the heat exchanger, the "dead space" is particularly small. Dead space or dead volume is understood to mean the space that does not take part in the change in volume. It is in particular the interior of the heat exchanger, a residual space in the chamber and, if appropriate, an airway section which lies between the heat exchanger and the intake or exhaust opening, for example to form a "neck" for air guidance.

In particular, the principle applies that the dead space is smaller, in particular considerably smaller, than the maximum volume of the chamber.

For proper functioning, it is not a hindrance if the piston element lies opposite the wall of the chamber, forming a gap. Although this leads to leakage losses, this is not relevant as long as the free opening area of the airway connected to the room is much larger than the gap cross-section. The gap formation ensures quiet operation since the components do not rub against each other.

The swivel angle of the displacement element moving in the manner of a flap is preferably in the range from 20 ° to 180 °.

As already mentioned above, the air path or the opening can have an air guide device, in particular a slot outlet provided with an air guide device. In this way, the direction of air discharge can be adjusted.

In particular, it is provided that the ventilation device is located on the ceiling and / or on the walls of the room to be ventilated. However, a design is also conceivable in which the ventilation system is located in the floor area, for example in a double floor of the room. To set the cooling or heating power, it is particularly simple to be able to adjust the frequency or the stroke or the swivel angle of the drive device in a controllable or regulatable manner. The higher the frequency and / or the larger the stroke and / or the larger the swivel angle, the more the air throughput and thus the cooling or heating capacity is greater.

The drive device for the piston element is formed in particular by a motor (electric motor), preferably a geared motor with an eccentric device. The eccentric device engages the piston element and thus enables the intermittent linear or intermittent pivoting movement.

The motor can preferably be designed as a DC motor. This has the advantage that an electrical speed control device can be connected which allows speed control or control in a particularly simple manner.

Alternatively, however, it is also possible for the drive device to be a solenoid or rotary magnet drive. An electric current is used to form a magnetic field that moves an armature back and forth, this movement being transmitted to the piston element. If a swiveling displacement element is used, the rotary magnet drive is advantageous.

A reset device can be assigned to the piston element. The drive device then only has the task of moving the piston element into its one end position. From this end position it is then moved into the other end position by means of the reset device. This can the drive device may be supporting. The resetting device preferably has a resetting spring. Additionally or alternatively, it is also possible to arrange the piston element in such a way that its return is effected or supported by gravity.

A particularly good efficiency can be achieved if the piston element is moved with its natural frequency or the system natural frequency formed by the resetting device and piston element and is not limited by a mechanical stop (for reasons of noise).

The ventilation device can be "double-acting". For this purpose, an air path leading into the room is assigned to the two sides of the piston element. If the piston element moves, this results in a volume increase on one side and a volume reduction in the corresponding chamber on the other side. When the piston element moves back, a correspondingly reverse process takes place.

In order to dampen the engine noise of the drive device particularly well, it is located outside the air flow.

If no purely recirculation mode is to be carried out with the ventilation system, the chamber interacts with a primary air supply. During the suction process, not only is room air in sucked the chamber, but also supplied primary air, so that both room air and primary air is blown into the room during the ejection process.

The invention further relates to the use of an air conveyor system according to one or more of the claims as a ventilation device for ventilating a room zone or a room. In addition to ventilation, air treatment can of course also be carried out.

Figur 1

eine schematische Ansicht einer lufttechnischen Einrichtung zum Heizen oder Kühlen eines Raumes,

Figur 2

eine Rückansicht auf eine mit Exzenterantrieb versehene Einrichtung,

Figur 3

die Einrichtung der Figur 2 in Seitenansicht,

Figur 4

ein Diagramm,

Figur 5

eine perspektivische Ansicht der in eine Decke eines Raumes eingebauten lufttechnischen Einrichtung,

Figur 6

eine schematische Darstellung einer lufttechnischen Einrichtung mit symmetrischem Luftaustritt,

Figur 7

eine lufttechnische Einrichtung mit Luftleiteinrichtung,

Figur 8

ein weiteres Ausführungsbeispiel einer Einrichtung gemäß Figur 7,

Figur 9

eine schematische Ansicht einer Kolbenelements-Variante der Einrichtung,

Figur 10

eine an einer Deckenstufe installierte Einrichtung,

Figur 11

eine an einem Luftleitschacht installierte Einrichtung,

Figur 12

eine lufttechnische Einrichtung mit Exzenterantrieb,

Figur 13

eine lufttechnische Einrichtung mit Drehmagnetantrieb,

Figur 14

eine Seitenansicht der Einrichtung gemäß Figur 13,

Figur 15

eine Einrichtung mit Hubmagnet-Antrieb,

Figur 16

eine Seitenansicht der Einrichtung gemäß Figur 15,

Figur 17

eine doppeltwirkende lufttechnische Einrichtung,

Figur 18

eine doppeltwirkende lufttechnische Einrichtung nach einem anderen Ausführungsbeispiel,

Figur 19

eine lufttechnische Einrichtung in senkrechter Einbaulage,

Figur 20

eine lufttechnische Einrichtung mit zusätzlicher Primärluftzuführung,

Figur 21

eine lufttechnische Einrichtung mit von der Schwenkachse entferntem Wärmetauscher,

Figur 22

eine lufttechnische Einrichtung mit mittig angeordnetem Wärmetauscher,

Figur 23

eine lufttechnische Einrichtung mit der Schwenkachse zugeordnetem Wärmetauscher,

Figur 24

eine lufttechnische Einrichtung mit zugeordneter Primärluftzuführung,

Figur 25

eine Einrichtung gemäß Figur 24, jedoch nach einem anderen Ausführungsbeispiel,

Figur 26

einen mit lufttechnischer Einrichtung versehenen Raum sowie zusätzlicher Primärluftzuführung,

Figur 27

eine Seitenansicht auf eine lufttechnische Einrichtung, die Bestandteil einer Torluftschleieranlage ist,

Figur 28

eine Unteransicht auf die Anlage gemäß Figur 27;

Figur 29

eine Stirnansicht auf die Anlage in Richtung des Pfeils in Figur 28,

Figur 30

eine lufttechnische Einrichtung, die für eine Abwärmenutzung eingesetzt ist,

Figur 31

eine lufttechnische Einrichtung, die nur der Förderung der Förderluft dient und keine Luftbehandlungseinrichtung aufweist,

Figur 32

eine lufttechnische Einrichtung mit LuftLeiteinrichtung,

Figur 33

eine andere Ausführungsform einer lufttechnischen Einrichtung mit Leiteinrichtung,

Figur 34

eine schematische Darstellung, die die Beeinflussung der Luftströmung in einem Raum demonstriert,

Figur 35

eine lufttechnische Einrichtung, der Primärluft zugeführt wird,

Figur 36

ein weiteres Ausführungsbeispiel entsprechend der Figur 35.

The drawings illustrate the invention using exemplary embodiments and show:

Figure 1

1 shows a schematic view of an air-conditioning device for heating or cooling a room,

Figure 2

a rear view of a device provided with an eccentric drive,

Figure 3

the device of Figure 2 in side view,

Figure 4

a diagram

Figure 5

1 shows a perspective view of the ventilation system built into a ceiling of a room,

Figure 6

1 shows a schematic representation of an air-conditioning device with a symmetrical air outlet,

Figure 7

an air-conditioning device with air guiding device,

Figure 8

another embodiment of a device according to Figure 7,

Figure 9

1 shows a schematic view of a piston element variant of the device,

Figure 10

a device installed on a ceiling step,

Figure 11

a device installed on an air duct,

Figure 12

a ventilation system with eccentric drive,

Figure 13

a ventilation system with a rotating magnet drive,

Figure 14

12 shows a side view of the device according to FIG. 13,

Figure 15

a device with solenoid drive,

Figure 16

2 shows a side view of the device according to FIG. 15,

Figure 17

a double-acting ventilation system,

Figure 18

a double-acting ventilation device according to another embodiment,

Figure 19

a ventilation system in a vertical installation position,

Figure 20

a ventilation system with additional primary air supply,

Figure 21

a ventilation system with a heat exchanger away from the swivel axis,

Figure 22

an air-conditioning device with a centrally located heat exchanger,

Figure 23

a ventilation system with a heat exchanger assigned to the swivel axis,

Figure 24

a ventilation system with an assigned primary air supply,

Figure 25

a device according to Figure 24, but according to another embodiment,

Figure 26

a room with ventilation equipment and additional primary air supply,

Figure 27

a side view of an air-conditioning device that is part of a door air curtain system,

Figure 28

a bottom view of the system of Figure 27;

Figure 29

3 shows a front view of the system in the direction of the arrow in FIG. 28,

Figure 30

a ventilation system that is used for waste heat recovery,

Figure 31

an air-conditioning device that only serves to convey the conveying air and has no air treatment device,

Figure 32

an air-conditioning device with air control device,

Figure 33

another embodiment of a ventilation device with a control device,

Figure 34

a schematic representation that demonstrates the influence of the air flow in a room,

Figure 35

a ventilation system to which primary air is supplied,

Figure 36

a further exemplary embodiment corresponding to FIG. 35.

FIG. 1 shows an exemplary embodiment of a ventilation device 1 for heating or cooling a room 2. The room 2 is in FIG. 1 only indicated with an arrow. It should be assumed that the ventilation device 1 is located within a suspended ceiling of the room 2. The visible ceiling 3 of the room 2 closes approximately flush with the underside 4 of a heat exchanger 5 of the ventilation device 1. The heat exchanger 5 is connected to a cold water source (cooling) or hot water source (heating).

A volume-changeable chamber 6 connects to the heat exchanger 5. The volume change takes place with a piston element 7, which can be moved in the directions of the double arrow 8. The movement takes place by means of a drive device 9 which has an electric motor 10 which drives an eccentric device 11. The eccentric device 11 is connected to the piston element 7 via a linkage 12.

According to the exemplary embodiment in FIG. 1, the piston element 7 is designed as a displacement element 14 which can be pivoted about an axis 13 in the manner of a flap. The axis 13 is located in the immediate vicinity of the upper edge 15 of the heat exchanger 5. The free end 16 of the displacement element 14 is opposed by a wall 18 of the chamber 6, forming a gap 17, the shape of the wall 18 being adapted to the movement curve of the displacement element 14 is. Parallel to the paper plane of FIG. 1 are further walls, not shown in the figure, on both sides of the displacement element 14 the chamber 6 arranged, which also leave a gap to the displacement element 14.

During operation (for example cooling), the displacement element 14, which is preferably plate-shaped, is pivoted from the angular position shown from approximately 25 ° to an end position in which it is parallel and at a short distance from the top side 19 of the heat exchanger 5. Here there is a reversal of movement and a pivoting back into the upper end position, etc. Air, which is located in the room 2, is due to the air conveyor system 20 thus formed through an air path 21, which is essentially formed by the heat exchanger 5, in the chamber 6 at the Volume increase sucked in and - in the assumed cooling case - cooled in a first step. If the eccentric device 1 then exceeds its top dead center, the chamber volume is reduced and the cooled air is expelled into the room 2 in the same way, that is to say again by passing through the airway 21 (but now in a different direction). When passing through the heat exchanger 5 there is a second step of cooling, the two cooling steps leading to the air being expelled having the desired temperature. Surprisingly, it has been shown that there is no short circuit between the sucked-in and expelled air, that is, the identical or almost identical air volume is not constantly sucked in and expelled again. Rather, the expelled air detaches as a vortex or as several vortices and penetrates into it Interior of the room. The air subsequently sucked in by the ventilation device 1 is therefore not identical to the expelled air, so that there is a recirculation mode. Due to the flap principle in the exemplary embodiment in FIG. 1, an excess velocity of the expelled air occurs on the right-hand side facing away from the axis of rotation 13, which preferably leads to a vortex formation offset to the right, i.e. away from axis 13, as is the case with the Reference numeral 22 is indicated. Because of this asymmetry, a particularly good eddy separation is achieved and a short-circuit effect is completely prevented. However, the asymmetrical design is not essential for the success of the invention, since - as will be shown later - no significant short-circuit effects occur even with symmetrical swirl output.

For the success according to the invention, it is also not necessary for the piston element to be moved periodically. Aperiodic movements are therefore also conceivable. These can be sinusoidal, but preferably also remain briefly at the end of the ejection phase or reduce the speed abruptly, which leads to very good vortex shedding. The faster the movement of the piston element 7 during the ejection process, the stronger the implus and the further the vortex will penetrate into the room. On the other hand, the opening movement of the flap (suction process) can take place relatively slowly. The air intake and exhaust process is indicated in FIG. 1 by means of the double arrows 23.

Since the piston element 7 is moved at a relatively low frequency (0.1 to a maximum of 30 Hz) and there is therefore an extremely low-frequency device, acoustically outstanding results are achieved. The electric motor 10 is also not in the air flow, so that motor noise is largely attenuated. A control or regulation of the recirculation mode and thus the heating or cooling output can be brought about by varying the speed of the piston element. The stroke also plays a crucial role. Furthermore, the dead volume. The dead volume is to be understood as the space that does not participate in the enlargement or reduction of the chamber 6. In the exemplary embodiment in FIG. 1, this is essentially the interior of the heat exchanger 5 that forms the air path 21. This dead volume should be as small as possible, in any case very much smaller than the maximum volume of the chamber 6. It is therefore less advisable to achieve an air throughput to be achieved with a small stroke and a large frequency, but to aim for the opposite case, namely a large stroke and a small frequency. The latter is limited by the increasing size.

In the chamber 6 there is hardly any mixing of the air, since the heat exchanger fins of the heat exchanger 5 act as a rectifier.

In Figures 2 and 3, the embodiment of Figure 1 is shown again in a variant. On the shaft connector 24 of the electric motor 10 there is a circular disk 25, from which an eccentric bolt 26 extends, which engages the linkage 12. The linkage 12 is pivotally attached to the displacement element 14.

Figure 2 shows that the chamber 6 extends over the entire depth of the heat exchanger 5, but not - according to Figure 3- only over the length of the heat exchanger 5, but even beyond. The base area of the chamber 6 adjoining the heat exchanger 5 is therefore larger than the base area of the heat exchanger 5. The arrangement is now such that the base area of the heat exchanger 5 is offset in the direction of the axis 13 with respect to the base area of the chamber 6. This leads to strong vortex formation with optimally detaching vertebrae.

FIG. 4 shows a diagram which shows the cooling capacity K and the volume flow V as a function of the stroke frequency f of the ventilation device 1. It can be seen that the volume flow V increases linearly in the frequency range indicated in FIG. The increase in cooling capacity K as a function of stroke frequency f is non-linear.

FIG. 5 shows a perspective view of the ventilation device 1 installed in the (cut) ceiling 3 of room 2. Clearly an opening 27 'can be seen in the ceiling 3, to which the heat exchanger 5 is adjacent. The blow-out vortices can be directed in a desired direction by means of suitable air guide elements (not shown). Such air guiding elements or outlet grids cause an additional pressure loss, but reduce the risk of a short circuit.

FIG. 6 shows, in a schematic representation, a further embodiment of an air-conditioning device 1 which, as piston element 7, has a plate 28 which is moved in translation. Drive training that cause such a movement are known to those skilled in the art, e.g. B. solenoids. Due to the symmetrical structure, symmetrical vortices 29, 30 will form during the air ejection process. Nevertheless, these vortices 29, 30 separate and penetrate into the room, so that the air subsequently sucked into the chamber 6 is not identical to the expelled air. Short circuits only occur to an insignificant extent. The vortex formation is supported if the orifices are arranged in the region of the inlet or outlet opening, that is to say in front of the heat exchanger 5 or at the edge of the heat exchanger 5. Such screens 31 are indicated in the exemplary embodiments in FIGS. 7 and 8. Because of these diaphragms 31, so-called stop vortices are formed, which detach in the best way.

FIG. 9 shows a further exemplary embodiment of a ventilation device 1, at which the piston element 7 is formed by a roller 32 which rolls back and forth in the chamber 6 by means of a suitable drive, as a result of which the chamber volume is increased or decreased.

The drive can - according to exemplary embodiments not shown - also correspond to how it z. B. in tool slides of horizontal shaping machines (z. B. planing machines) is known. This leads to a very rapid ejection movement of the air and, in contrast, a slower suction movement.

FIG. 10 shows an embodiment of the invention which corresponds to the embodiment of FIGS. 2 and 3. Only the differences will be discussed below. These differences exist in the design of the ceiling 3 of the room 2. In the area assigned to the axis 13 of the pivotable displacement element 14, a step 33 is formed on the ceiling 3, that is to say the ceiling height of the room 2 is smaller in the area of the heat exchanger 5 than in Connection to level 33. Level 33 has a fluidic effect, in which it "attracts" ejected vortices, ie deflects them accordingly. This is beneficial for avoiding short-circuit effects. So-called vortices are formed, which run along the ceiling and allow the cooled air to penetrate far into room 2.

In the exemplary embodiment in FIG. 11, the ceiling 3 of the room 2 in the area of the heat exchanger 5 is provided with a neck 34 which is directed towards the ejected ones Vertebra exerts a directional effect. The expelled vortices therefore penetrate downward into space 2. This is particularly important when introducing warm air.

The exemplary embodiment in FIG. 12 again shows a design with a “pivoting piston”. There it is made clear that the eccentric device 11 can be provided with a counterweight 35 which is diametrically offset from the articulation point 37 of the linkage 12 with respect to the axis of rotation of the drive device. As a result, vibrations, which can be triggered by an unsteady run, are largely avoided.

FIGS. 13 and 14 show a ventilation device 1 which, in contrast to the embodiments of the previous exemplary embodiments, is not provided with an eccentric drive, but with a rotary magnet drive 38. The rotary magnet drive 38 is placed directly on the axis 13 of the pivotable displacement element 14. For example, a swivel angle of 45 ° can be realized. By directly flanging the rotary magnet drive 38 on the axis 13, transverse forces acting on the flap bearing are avoided. The rotary magnet drive 38 is controlled by means of a corresponding electrical control device, so that the desired movement (acceleration, speed, swivel range, etc.) is established.

The exemplary embodiment in FIG. 13 shows a reset device 42. This reset device 42 is realized by means of a return spring 43, which is designed as a tension spring and is fixedly attached at one end to the displacement element 14 and at the other end. It causes the pivotable displacement element 14 to be returned in the direction of the top dead center position. Instead of the embodiment shown in FIG. 13, reset devices are also conceivable which are based additionally or exclusively on the principle of gravity, that is to say because of the weight of the piston element 7, it is moved back into an initial position.

The flap-shaped displacement element 14 can oscillate at the natural frequency of the system consisting of the return spring 43 and the mass of the "flap". The vibrations are excited by means of a corresponding magnetic excitation of the rotary magnet 38. The strength of the coil current of the rotary magnet 38 determines the strength of the excitation. It is necessary to cycle the excitation according to the valve position. The system is dampened by air resistance.

Alternatively, the embodiment of FIG. 13 is also possible without a reset device 42.

FIGS. 15 and 16 show a further variant of an elector-magnetic drive, in which lifting magnets 39 are used. As in the case of the rotary magnet drive 38 in FIGS. 13 and 14, the lifting magnets 39 in the exemplary embodiment in FIGS. 15 and 16 are passed through by means of corresponding coils electrical current flow formed. The axis 13 of the displacement element 14 is connected in a rotationally fixed manner to a double lever 40, at each end of which one of the two lifting magnets 39 engage by means of actuating rods 41. By appropriate actuation of the lifting magnets 39, in that one lifting magnet 39 presses and the other pulls, a pivoting movement of the displacement element 14 is generated by a torque on the axis 13 that is free of lateral forces.

It is particularly advantageous if the piston element 7 is made very light, for example is made of a plate in sandwich construction with a honeycomb structure. Plastic-laminated hard foam panels or thin-walled shell constructions can also be used.

In the electromagnetic drives mentioned, it can always be provided that neither the armature nor the displacement element strikes against other components. This is possible by means of a suitable control / regulation of the excitation current.

FIG. 17 shows a double-acting ventilation device 1. This has two heat exchangers 5 arranged at an obtuse angle to one another, to which a double chamber or each chamber 6 is assigned. The piston element 7 is designed as a pivotable displacement element 14, the axis 13 being located in the lower region between the two heat exchangers 5. Via corresponding airways 48, in which air guiding elements 49 are located can, the heat exchangers 5 are connected to the room 2. A swiveling movement of the displacement element 14 causes an increase in volume on one side and a decrease in volume on the other side. This means that air is sucked in from the room 2 through the one heat exchanger 5 and air is blown into the room 2 through the other heat exchanger 5 through the other heat exchanger 5 by volume reduction - on the other side of the displacement element 14.

FIG. 18 shows a further embodiment of a double-acting ventilation device 1. In contrast to the embodiment of FIG. 14, this has only one heat exchanger 5, which, however, is assigned to a double chamber. For this purpose, the axis 13 of the displacement element 14 lies approximately in the middle of the heat exchanger 5, so that in each case approximately half of the heat exchanger 5 is used for the suction and the simultaneous ejection process of each chamber 6.

FIG. 19 only shows a different installation position of the ventilation device 1 compared to the previously mentioned exemplary embodiments. Here, the ventilation device 1 is arranged vertically, that is, it can be installed in a wall of the room 2, for example. The axis of rotation 13 of the displacement element 14, which can be pivoted in the manner of a flap, is preferably arranged at the bottom, that is to say the flap is not mounted in a hanging manner but in an upright position.

The embodiment of Figure 20 differs from that of Figure 1 in that the flap-shaped displacement element 14 has a check valve 50, for example also in the form of a flap. A further chamber 51, which is connected to primary air P, is formed above the displacement element 14. This primary air P can be pressureless or pressurized. If - according to FIG. 20 - the displacement element 14 is pivoted upward, the check valve 50 opens so that primary air can flow into the chamber 6. This is in addition to the air drawn in from room 2. When the displacement element 14 moves downward, the check valve 50 then closes, so that both the air drawn in from the room 2 and the primary air in the chamber 6 are expelled into the room 2. Thus, in the exemplary embodiment in FIG. 20, there is no pure recirculation mode, but rather recirculation mode and primary air mode.

FIGS. 21 to 23 show exemplary embodiments of the invention in which the heat exchanger 5 is in a different position. The device design of FIGS. 21 to 23 corresponds to that of FIG. 3, so that reference is made to it. In the exemplary embodiment in FIG. 21, the heat exchanger 5 is arranged away from the axis 3. It borders with its end opposite the axis 13 to the corresponding wall of the chamber 6. In the exemplary embodiment in FIG. 22, the heat exchanger 5 is located approximately in the center of the base area of the chamber 6, ie there is also a distance from it Axis 13, which is, however, smaller than in the exemplary embodiment in FIG. 21. In the exemplary embodiment in FIG. 23, the heat exchanger 5 borders directly on the axis 13; it is at a distance from the wall of the chamber 6 opposite the axis 13.

FIG. 24 shows an air-conditioning device 1 according to an arrangement of FIG. 10, that is, there is a step 33 in the ceiling 3 of room 2. The step 33 has a vertical wall 55. The heat exchanger 5 is at a distance x from the lower edge of the wall 55. A primary air outlet 56, which leads to a primary air chamber 57, to which primary air P is supplied, opens into the wall 55. The vortices formed by the ventilation device 1 pass through the stage 22 and meet the primary air P there. This can have a slight overpressure and thus penetrate into the room 2. However, it is alternatively or additionally also possible that the vortices promote the primary air P by induction.

FIG. 25 shows a further exemplary embodiment of a ventilation device 1, in which a primary air device is also used. This has a primary air outlet 56, which opens into the ceiling 3 of the room 2. The primary air outlet 56 leads to a primary air chamber 57, which is supplied with primary air P. The arrangement is such that the primary air outlet 56 is on the side of the heat exchanger 5 of the ventilation device 1, which is opposite to Flow direction of the ejected vortices of the ventilation device 1 is.

FIG. 26 shows a room 2 of a building or the like, which is provided with a ventilation device 1. This is located under a cladding 58 in a corner area, which is formed by a wall and the floor of the room 2. The cladding 58 has an outlet opening 60 in the horizontal region 59 and an inlet opening 61 in the region of the floor. Under the cladding 58 there is the ventilation device 1 and a primary air device 62. This has a primary air outlet 56 which opens approximately in the area between the inlet opening 61 and the heat exchanger 5 of the ventilation device 1.

During operation of the arrangement according to FIG. 26, an "air roller" with cold or warm eddies (cooling mode or heating mode) forms in room 2, which is excited by air escaping from air outlet opening 60. This rises to the ceiling of the room and moves in the direction of the opposite wall 63. The air flow then drops again towards the floor and is finally sucked into the inlet opening 61. The primary air device 62 can be an air distribution box provided with nozzles. The nozzles steer a motive air volume flow upwards in the direction of the outlet opening 60. The motive air volume flow can preferably be an outside air volume flow, especially with constant air temperature throughout the year.

The heat exchanger 5 of the above exemplary embodiments can be of a design with an increased fin thickness and increased fin spacing. This is possible because of the double passage of air (during suction and when discharging). There is a high level of heat transfer; only thin boundary layers form on the fins. Such heat exchangers are very easy to clean; there is only a slight tendency to dirt accumulation. Furthermore, it is also conceivable that a coating with dirt-repellent lacquer is provided. As a result, there is little dust storage. This leads to advantageous long maintenance intervals and also prevents self-odor. Furthermore, it is also possible to provide only a small slat height due to the circumstances mentioned above, so that the dead space is very small.

As shown in FIG. 26, a primary air device 62 can be provided so that no pure recirculation mode takes place, but fresh air is added. However, it is of course also possible that no primary air device 62 is provided.

FIG. 27 shows a door air curtain system 70 which has two ventilation devices 1, which has an air duct 71 arranged above a door opening (not shown). This air duct 71 has outlet openings 73 on its underside 72, so that the air located in the air duct 71 can emerge from these outlet openings 73 and form the air curtain. It can be seen from FIG. 28 that the air duct 71 has three rows of outlet openings 73 running parallel to one another. It is of course also possible that, for example, only a central row of outlet openings 73 is provided.

According to FIGS. 27 and 29, the volume-variable chamber 6, which has a heating register 74 in its air path 21 and forms an air treatment device 5 ', is arranged above the air duct 71 - in each of the air technology devices 1-.

During operation of the door air curtain system 70, air present in the area of the door is sucked in by reducing the volume of the chambers 6, the air passing through the heating register 74 and then being introduced into the air duct 71 by reducing the volume of the chambers 6 and passing through the heating register 74 again, and then from the outlet openings 73 to generate the air curtain.

FIG. 30 shows an exemplary embodiment in which an air-technical device 1 is assigned to an air line 75, which has air with the temperature σ _E upstream. A heat exchanger 5 is assigned to the jacket wall of the air line 75 and connects it to the chamber 6 of the air technology Device 1. The heat exchanger 5 is connected to a circuit 76 which serves to remove waste heat for the desired purposes. During operation, air present in the air line 75 is sucked in with the temperature σ _E and thus passes into the chamber 6 while passing the heat exchanger 5. When this air is expelled from the chamber 6 in the direction of the air line 75, this air again passes through the heat exchanger 5 with discharge of temperature and finally gets back into the air line 75, where it then has a downstream temperature σ _A , which is less than the temperature σ _E. This reduction in temperature is caused by the fact that heat has been given off to the heat exchanger 5 and is used for use by means of the circuit 76.

FIG. 31 explains - in a basic embodiment - an air-technical device 1 which serves as a pure air conveying system, that is to say, in the course of its recirculating air operation, air is admitted into a room 2 or a room zone 2 'of the room 2 via the air path 21 which merely forms an opening Inside the chamber 6 sucked and then ejected again. This allows, for example, effective room air mixing. A proportion of primary air (or a material flow admixture of any kind) can also be provided, corresponding to the exemplary embodiment in FIGS. 24, 25, 26, 35 and 36. An air treatment device 5 ', such as that mentioned in the above-mentioned exemplary embodiments Represents heat exchanger 5, is therefore not present in the embodiment of Figure 31.

The shape of the wall 18, which forms a wall of the chamber 6, has an influence on the production and on the formation of the exhaust vortices. The geometry can therefore be chosen by a person skilled in the art in such a way that ejection vortices are set in the desired manner.

As already mentioned above, the heat exchanger 5 represents an air treatment device 5 ', which was exemplified in the above exemplary embodiments. It is of course possible to use other types of air treatment devices 5 'instead of the heat exchanger 5, for example devices of this type which influence the air humidity. It is also possible to use material conversion devices, for example catalysts, which also carry out air treatment.

Finally, it should be mentioned that in the exemplary embodiments shown in the figures, air-technical devices 1 can also be used which do not have an air treatment device 5 'or a heat exchanger 5 or the like.

In the exemplary embodiment in FIG. 32, the air treatment device 5 ′ designed as a heat exchanger 5 is followed by a guide device 80 which, for example, has a circular outlet opening 81 having. It can be seen how toroidal air swirls 82 are ejected from the outlet opening 81. A total of three components are thus essentially provided in the air-technical device 1, namely on the one hand the air delivery system (chamber 6, piston element 7), air treatment device 5 'and guide device 80. These components can also be implemented separately so that they have to be put together at the place of use.

In FIG. 33, a swivel piston element is provided instead of the piston element 7 of FIG. 32 that is to be moved linearly.

The air guide device 80 makes it possible to influence the type and / or the direction of the vortices to be ejected.

With the overall arrangement, it is therefore possible to influence the air flow in a room 2 or in a room zone 2 '. If a certain level of comfort is to be created, for example, in a living room, the procedure is such that the vortices have a not too great ejection pulse and a not too high outlet speed, as a result of which - according to FIG. 34 - cool vortices 83 are ejected, between which there is warm room air 84 is located. Due to the relatively low outlet speed, there is a correspondingly high induction, as a result of which a very good air mixture is achieved when the vortex disintegrates. For example, it is also possible to easily corner the room ventilated with comfort to create a comfortable atmosphere. The ventilation method according to the invention is particularly advantageous over known jet ventilation because, unlike jet ventilation, there is no Coanda effect on boundary walls, for example on the ceiling and / or room wall.

The invention is self-evident and preferably also used in process air technology, for example in order to act against the heat interference field, for example of a machine. In this case, vortices with a relatively high ejection pulse and thus with a high outlet speed are ejected, for example to work against a thermal originating, for example, from a textile or weaving machine. It is possible to break up this thermal field with the ejection vortices emitted by the device according to the invention and, in this respect, to bring about optimal ventilation even under these difficult conditions. Such a good ventilation result cannot be achieved by means of the known jet ventilation, because an air jet is very quickly consumed and / or pushed away due to the interference field.

With the pulse ventilation according to the invention, a very high heat exchange can be achieved, which is about 30% higher than in conventional systems.

FIG. 35 illustrates an exemplary embodiment with a pivoting piston 7, with a further chamber 85 adjoining the chamber 6, into which preferably radially a primary air connection 86 opens. The air treatment device 5 ′, which is followed by a guide device 80, preferably adjoins the chamber 86. FIG. 36 shows a corresponding exemplary embodiment with linearly moving piston 7. In the exemplary embodiments in FIGS. 35 and 36, primary air can thus be admixed to the air conveyed in the recirculating air principle, that is to say both primary air and recirculated air operation take place. It is also possible to introduce any material flow in addition to or instead of the primary air, for example air provided with fragrance components or certain gases, etc.

Instead of the pivoting piston 7 or the linear piston 7 in the exemplary embodiments in FIGS. 35 and 36 or the piston shown in one of the exemplary embodiments of the invention, it is also possible, for example, to use a membrane or the like which is in motion, that is to say in vibration, by means of a drive device , is set, creating a chamber, is sucked into the air and expelled again. Such a membrane can, for example, also be set to vibrate by electromagnetic means, the "loudspeaker principle", whereby an air conveyor system is formed overall.

Claims (37)

1. A ventilation device having an air conveyor arrangement (20) for supplying a spatial area with conveyed air, the air conveyor arrangement (20) conveying in a pulsed manner at least a portion of the conveyed air in a circulating operation by means of at least one chamber (6) which has a variable volume and which is connected by way of at least one ventilation path (21) to the spatial area (2'), characterized in that one and the same ventilation path (21) forms both an air intake path and an air discharge path.
2. A ventilation device according to Claim 1, characterized in that, by means of the air conveyor arrangement (20), when the air is discharged eddies are produced which have an angular and a translational momentum at least great enough for them to separate and penetrate into the spatial area (2').
3. A ventilation device according to one of the preceding claims, characterized in that, by means of the air conveyor arrangement (20), when the air is discharged a pulsating flow is produced which is of high enough energy for it to separate and penetrate into the spatial area (2').
4. A ventilation device according to one of the preceding claims, characterized in that a drive device (9) is provided for varying the volume of the chamber (6), which drive device (9) operates at a frequency in the range of 0.1 to 30 Hz.
5. A ventilation device according to one of the preceding claims, characterized by an air treatment facility (5') which is located in the ventilation path (21).
6. A ventilation device according to one of the preceding claims, characterized in that the air treatment facility (5') is constructed as a heat exchanger (5) and/or an air humidity influencing device and/or as a substance converting device, in particular a catalyst.
7. A ventilation device according to one of the preceding claims, characterized in that the ventilation path (21) is constructed as an opening having the air treatment facility (5') linked thereto.
8. A ventilation device according to one of the preceding claims, characterized in that, for varying the volume, a piston element (7) is arranged in the chamber (6).
9. A ventilation device according to one of the preceding claims, characterized in that the piston element (7) is constructed as a piston which is moved in translation.
10. A ventilation device according to one of the preceding Claims 1 to 9, characterized in that the piston element (7) is constructed as a displacer element (14) which is pivotal about an axis (13) in the manner of a flap.
11. A ventilation device according to one of the preceding claims, characterized in that the walls of the chamber (6) are shaped to match the curved movement of the displacer element (14).
12. A ventilation device according to one of the preceding claims, characterized in that the piston element (7) is constructed to be plate-shaped.
13. A ventilation device according to one of the preceding claims, characterized in that the rate of movement and/or the acceleration of the piston element (7) and/or the stroke travel and/or the frequency of movement may be varied, in particular may be adjusted to a selected value, and in particular are set to this value.
14. A ventilation device according to one of the preceding claims, characterized in that the size of the angle of pivoting of the displacer element (14) may be varied, in particular may be adjusted to a selected value, and in particular is set to this value.
15. A ventilation device according to one of the preceding claims, characterized in that that floor area of the chamber (6) which adjoins the air treatment facility (5') is larger than the floor area of the air treatment facility (5').
16. A ventilation device according to one of the preceding claims, characterized in that the air treatment facility (5') has a ventilation opening which, with respect to the larger, adjoining floor area of the chamber (6), is arranged offset in the direction towards the pivot axis (13) of the displacer element (14).
17. A ventilation device according to Claim 14, characterized in that the ventilation opening in the air treatment facility (5') adjoins the pivot axis (13).
18. A ventilation device according to one of the preceding claims, characterized in that, in the position at which its pivotal movement is reversed, at the end of the discharge phase, the displacer element (14) directly adjoins the air treatment facility (5').
19. A ventilation device according to one of the preceding claims, characterized in that the dead space, that is to say the space whereof the volume may not be varied, is small in relation to the maximum volume of the chamber (6).
20. A ventilation device according to one of the preceding claims, characterized in that the piston element (7) is opposite the wall of the chamber (6), forming a gap (17).
21. A ventilation device according to one of the preceding claims, characterized in that angle of pivoting of the displacer element (14) is in the range from 20° to 180°.
22. A ventilation device according to one of the preceding claims, characterized in that the ventilation path (21), or the opening, has an air deflecting device (27), in particular a slot-type outlet provided with an air deflecting device.
23. A ventilation device according to one of the preceding claims, characterized in that it is arranged on the ceiling (3) and/or on the walls of a room (2) having the spatial area (2').
24. A ventilation device according to one of the preceding claims, characterized in that the frequency and/or the stroke travel and/or the angle of pivoting of the drive device (9) may be controlled or set to adjust the air treatment intensity.
25. A ventilation device according to one of the preceding claims, characterized in that the drive device (9) is constructed as a motor (preferably an electric motor), in particular a gear motor having an eccentric means acting on the piston element (7).
26. A ventilation device according to one of the preceding claims, characterized in that the motor is a d.c. motor.
27. A ventilation device according to one of the preceding claims, characterized in that the d.c. motor is linked to an electrical speed-control device.
28. A ventilation device according to one of the preceding claims, characterized in that the drive device (9) is a solenoid drive or a moving-magnet drive (solenoids 39, moving-magnet drive 38).
29. A ventilation device according to one of the preceding claims, characterized in that a resetting facility (42) is associated with the piston element (7).
30. A ventilation device according to one or more of the preceding claims, characterized in that the resetting facility (42) has at least one resetting spring (43).
31. A ventilation device according to one of the preceding claims, characterized in that the piston element (7) is arranged mounted in a manner such that its resetting action is effected or supported by gravity.
32. A ventilation device according to one of the preceding claims, characterized in that the piston element (7) is moved by its natural frequency or the natural frequency of the system created by the resetting facility (42) and the piston element (7).
33. A ventilation device according to one of the preceding claims, characterized in that associated with the two sides of the piston element (7) there is in each case a ventilation path (21) leading into the spatial area (2'), and in that associated with the two sides of the piston element (7) there is in each case a chamber (6) which is variable in its volume.
34. A ventilation device according to one of the preceding claims, characterized in that the drive device (9) is located outside the air flow.
35. A ventilation device according to one of the preceding claims, characterized in that a primary-air supply interacts with the chamber (6).
36. A ventilation device according to one of the preceding claims, characterized in that it has only one ventilation path (21).
37. The use of a ventilation device, according to one or more of the preceding claims, for ventilating a spatial area (2') or a room (2).

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