EP0681674B1 - Lufttechnische einrichtung - Google Patents

Lufttechnische einrichtung Download PDF

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Publication number
EP0681674B1
EP0681674B1 EP94906171A EP94906171A EP0681674B1 EP 0681674 B1 EP0681674 B1 EP 0681674B1 EP 94906171 A EP94906171 A EP 94906171A EP 94906171 A EP94906171 A EP 94906171A EP 0681674 B1 EP0681674 B1 EP 0681674B1
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EP
European Patent Office
Prior art keywords
air
ventilation device
ventilation
chamber
piston element
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP94906171A
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German (de)
English (en)
French (fr)
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EP0681674A1 (de
Inventor
Hans-Werner Roth
Andreas Böllinger
Gerd-Eugen Schaal
Claus Händel
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LTG Lufttechnische GmbH
Original Assignee
LTG Lufttechnische GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE4302855A external-priority patent/DE4302855C1/de
Priority claimed from DE19934310959 external-priority patent/DE4310959C1/de
Application filed by LTG Lufttechnische GmbH filed Critical LTG Lufttechnische GmbH
Publication of EP0681674A1 publication Critical patent/EP0681674A1/de
Application granted granted Critical
Publication of EP0681674B1 publication Critical patent/EP0681674B1/de
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/26—Arrangements for air-circulation by means of induction, e.g. by fluid coupling or thermal effect
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15D—FLUID DYNAMICS, i.e. METHODS OR MEANS FOR INFLUENCING THE FLOW OF GASES OR LIQUIDS
    • F15D1/00—Influencing flow of fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15D—FLUID DYNAMICS, i.e. METHODS OR MEANS FOR INFLUENCING THE FLOW OF GASES OR LIQUIDS
    • F15D1/00—Influencing flow of fluids
    • F15D1/009—Influencing flow of fluids by means of vortex rings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0011—Indoor units, e.g. fan coil units characterised by air outlets
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/0007—Indoor units, e.g. fan coil units
    • F24F1/0043—Indoor units, e.g. fan coil units characterised by mounting arrangements
    • F24F1/0047—Indoor units, e.g. fan coil units characterised by mounting arrangements mounted in the ceiling or at the ceiling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/02—Ducting arrangements
    • F24F13/06—Outlets for directing or distributing air into rooms or spaces, e.g. ceiling air diffuser

Definitions

  • 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).
  • Ventilation equipment 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • a device which influences the air humidity can be used as the air treatment device.
  • a substance conversion device for example a catalyst, which influences the air conveyed.
  • 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.
  • the piston element can be designed as a translationally moved piston.
  • the piston element can be designed 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.
  • the frequency of movement of the piston element and / or the stroke can be varied and can thus be set to a desired value.
  • the base area of the chamber adjoining the heat exchanger can be larger than the base area of the heat exchanger.
  • 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.
  • the principle applies that the dead space is smaller, in particular considerably smaller, than the maximum volume of the chamber.
  • the swivel angle of the displacement element moving in the manner of a flap is preferably in the range from 20 ° to 180 °.
  • 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.
  • the ventilation device is located on the ceiling and / or on the walls of the room to be ventilated.
  • 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.
  • the drive device may 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.
  • the chamber interacts with a primary air supply.
  • a primary air supply 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.
  • air treatment can of course also be carried out.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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).
  • the two cooling steps leading to the air being expelled having the desired temperature.
  • 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.
  • 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.
  • the piston element 7 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.
  • 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.
  • Figures 2 and 3 the embodiment of Figure 1 is shown again in a variant.
  • 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.
  • the blow-out vortices can be directed in a desired direction by means of suitable air guide elements (not shown).
  • 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.
  • 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.
  • 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.
  • FIG. 12 again shows a design with a “pivoting piston”.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • this has only one heat exchanger 5, which, however, is assigned to a double chamber.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • an "air roller" with cold or warm eddies 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.
  • 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.
  • FIG. 28 shows 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.
  • 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 ⁇ 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.
  • air present in the air line 75 is sucked in with the temperature ⁇ E and thus passes into the chamber 6 while passing the heat exchanger 5.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • 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.
  • a membrane can, for example, also be set to vibrate by electromagnetic means, the "loudspeaker principle", whereby an air conveyor system is formed overall.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • Air-Flow Control Members (AREA)
  • Seal Device For Vehicle (AREA)
  • Liquid Crystal (AREA)
  • Input Circuits Of Receivers And Coupling Of Receivers And Audio Equipment (AREA)
  • Ventilation (AREA)
  • Compressor (AREA)
  • Percussion Or Vibration Massage (AREA)
  • Filtering Of Dispersed Particles In Gases (AREA)
  • Building Environments (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)
  • Jet Pumps And Other Pumps (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Current-Collector Devices For Electrically Propelled Vehicles (AREA)
  • Discharge Heating (AREA)
  • Emergency Protection Circuit Devices (AREA)
  • Control Of Eletrric Generators (AREA)
  • Steering-Linkage Mechanisms And Four-Wheel Steering (AREA)
  • Glass Compositions (AREA)
  • Reciprocating Pumps (AREA)
  • Magnetically Actuated Valves (AREA)
  • Power Steering Mechanism (AREA)
EP94906171A 1993-02-02 1994-01-29 Lufttechnische einrichtung Expired - Lifetime EP0681674B1 (de)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE4302855A DE4302855C1 (de) 1993-02-02 1993-02-02 Lufttechnische Einrichtung zum Heizen oder Kühlen eines Raumes
DE4302855 1993-02-02
DE4310959 1993-04-03
DE19934310959 DE4310959C1 (de) 1991-10-08 1993-04-03 Luftauslaß
PCT/EP1994/000256 WO1994018506A1 (de) 1993-02-02 1994-01-29 Lufttechnische einrichtung

Publications (2)

Publication Number Publication Date
EP0681674A1 EP0681674A1 (de) 1995-11-15
EP0681674B1 true EP0681674B1 (de) 1996-09-11

Family

ID=25922716

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EP94906171A Expired - Lifetime EP0681674B1 (de) 1993-02-02 1994-01-29 Lufttechnische einrichtung

Country Status (24)

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US (1) US5690165A (hu)
EP (1) EP0681674B1 (hu)
JP (1) JPH08506174A (hu)
KR (1) KR100313262B1 (hu)
CN (1) CN1083087C (hu)
AT (1) ATE142767T1 (hu)
AU (1) AU674388B2 (hu)
BR (1) BR9405877A (hu)
CA (1) CA2155026A1 (hu)
CZ (1) CZ289611B6 (hu)
DE (1) DE59400639D1 (hu)
EG (1) EG20784A (hu)
ES (1) ES2094646T3 (hu)
FI (1) FI111988B (hu)
GR (1) GR3021857T3 (hu)
HU (1) HU218751B (hu)
IL (1) IL108468A (hu)
NO (1) NO301137B1 (hu)
PL (1) PL173636B1 (hu)
RU (1) RU2118761C1 (hu)
TR (1) TR29001A (hu)
TW (1) TW248586B (hu)
UA (1) UA52578C2 (hu)
WO (1) WO1994018506A1 (hu)

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19646561C2 (de) * 1996-11-12 2002-01-03 Hoval Interliz Ag Vaduz Verfahren und Vorrichtung zum Erzeugen eines Fluidstroms
NO316474B1 (no) * 2002-04-25 2004-01-26 Jan Roger Stokke Kjöleanordning
DE502008002644D1 (de) * 2008-12-15 2011-03-31 Siemens Ag Schwingmembranlüfter mit gekoppelten Teileinheiten, und Gehäuse mit einem derartigen Schwingmembranlüfter
JP5359458B2 (ja) * 2009-03-27 2013-12-04 ダイキン工業株式会社 空気調和装置、ケーシング、および化粧パネル
DE202009015728U1 (de) 2009-12-14 2010-05-12 Wang, Tian Shoei, Shaluh Parallel klemmendes Handwerkzeug
US20110283986A1 (en) * 2010-05-20 2011-11-24 Sergiy Lozovsky Apparatus for Improved Efficiency of an Air Conversion Device
WO2012065193A1 (en) * 2010-11-08 2012-05-18 Chi Tran Dissipating wind surface in electric fans of box type
US10016335B2 (en) * 2012-03-27 2018-07-10 Electromed, Inc. Body pulsating apparatus and method
US9243622B2 (en) * 2013-05-22 2016-01-26 The Boeing Company Bellows synthetic jet
US9682388B2 (en) 2014-12-05 2017-06-20 Elwha Llc Using vortex rings to deliver gases at a distance
CN106151878A (zh) * 2015-03-24 2016-11-23 启碁科技股份有限公司 磁浮式气流交换的方法及磁浮式气流交换系统
WO2018208640A1 (en) * 2017-05-10 2018-11-15 Pepsico, Inc. Hot airflow management systems and methods for coolers

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DE147982C (hu) *
US584154A (en) * 1897-06-08 Hand-bellows
BE534042A (hu) * 1954-11-19
US2888870A (en) * 1955-02-23 1959-06-02 Drager Otto Heinrich Sand or earth filter for shelters
CH355695A (de) * 1955-02-23 1961-07-15 Draeger Otto Heinrich Dr Luftschutzraum mit mindestens einer Filteranordnung zur Filtration der einzuführenden Luft
US2991763A (en) * 1959-07-27 1961-07-11 Weatherhead Co Actuator
US3804364A (en) * 1971-07-28 1974-04-16 Danfoss As Bag diaphragms and bag diaphragm operated air dampers
US4232211A (en) * 1978-10-19 1980-11-04 Hill Johnnie L Automobile auxiliary heater
JPS61256127A (ja) * 1985-05-07 1986-11-13 Matsushita Electric Ind Co Ltd 空気調和機のフイルタ装置
JPS625030A (ja) * 1985-06-28 1987-01-12 Matsushita Electric Ind Co Ltd 換気装置
US4952283A (en) * 1988-02-05 1990-08-28 Besik Ferdinand K Apparatus for ventilation, recovery of heat, dehumidification and cooling of air
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JPH03249383A (ja) * 1990-02-28 1991-11-07 Mori Seisakusho:Yugen 空気清浄機の送風方法及びその送風装置
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Also Published As

Publication number Publication date
AU674388B2 (en) 1996-12-19
FI111988B (fi) 2003-10-15
DE59400639D1 (de) 1996-10-17
CZ16794A3 (en) 1994-08-17
IL108468A (en) 1997-02-18
GR3021857T3 (en) 1997-03-31
FI953610A0 (fi) 1995-07-28
JPH08506174A (ja) 1996-07-02
ATE142767T1 (de) 1996-09-15
HU218751B (hu) 2000-11-28
NO952922D0 (no) 1995-07-24
TW248586B (hu) 1995-06-01
HU9502020D0 (en) 1995-09-28
CN1117312A (zh) 1996-02-21
PL309405A1 (en) 1995-10-02
PL173636B1 (pl) 1998-04-30
AU5999894A (en) 1994-08-29
HUT71830A (en) 1996-02-28
US5690165A (en) 1997-11-25
CN1083087C (zh) 2002-04-17
NO301137B1 (no) 1997-09-15
TR29001A (tr) 1997-08-06
NO952922L (no) 1995-07-24
CZ289611B6 (cs) 2002-03-13
BR9405877A (pt) 1995-12-12
FI953610A (fi) 1995-07-28
UA52578C2 (uk) 2003-01-15
EG20784A (en) 2000-02-29
WO1994018506A1 (de) 1994-08-18
RU2118761C1 (ru) 1998-09-10
EP0681674A1 (de) 1995-11-15
ES2094646T3 (es) 1997-01-16
CA2155026A1 (en) 1994-08-18
IL108468A0 (en) 1994-04-12
KR100313262B1 (ko) 2002-06-26

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