EP0531508B1 - Vorrichtung zur raumtemperatursteuerung - Google Patents

Vorrichtung zur raumtemperatursteuerung Download PDF

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Publication number
EP0531508B1
EP0531508B1 EP92909650A EP92909650A EP0531508B1 EP 0531508 B1 EP0531508 B1 EP 0531508B1 EP 92909650 A EP92909650 A EP 92909650A EP 92909650 A EP92909650 A EP 92909650A EP 0531508 B1 EP0531508 B1 EP 0531508B1
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EP
European Patent Office
Prior art keywords
air
blowing
convergent element
suction
upstream
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EP92909650A
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English (en)
French (fr)
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EP0531508A1 (de
Inventor
Edmond Montaz
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Spirec A Responsabilite Ltee Ste
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Spirec A Responsabilite Ltee Ste
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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
    • 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
    • F24F13/04—Air-mixing units
    • 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
    • F24F13/24—Means for preventing or suppressing noise
    • 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
    • F24F13/08—Air-flow control members, e.g. louvres, grilles, flaps or guide plates
    • F24F13/082—Grilles, registers or guards
    • F24F2013/088—Air-flow straightener
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2221/00—Details or features not otherwise provided for
    • F24F2221/14—Details or features not otherwise provided for mounted on the ceiling

Definitions

  • the present invention relates to a device intended to regulate the temperature of a room using an air flow, at a given temperature, pulsed therein.
  • a first drawback comes from the noise produced by the installation. Indeed, we know that the noise produced by an air conditioning installation depends, on the one hand, on the noise produced by the air streams moving on the walls of the ventilation ducts, noise which is directly linked to the speed of the fluid in contact with this wall and, on the other hand, that produced by the blowing in the room, which depends on the speed of the air arriving in it.
  • a second drawback stems from the fact that, in winter, the forced air, warmer than the ambient air, goes towards the ceiling and, in summer, the forced air, cooler than the ambient air, becomes go to the floor of the room.
  • This difference in temperature in the systems according to the prior art being relatively large, it therefore results, summer and winter, a permanent movement of the air at the interior of the room which, in addition to the own blowing speed of this air, is likely to cause discomfort to the user by the air flow it forms.
  • the temperature gradient existing between the floor and the ceiling of the room which is all the more important as the temperature difference between the blown air and the ambient air is large, is also likely to cause discomfort to the user.
  • VMC ventilation device
  • air leaks existing between the room and the outside we also know that, in a room, part of the forced air flow is evacuated to the outside, for example by a ventilation device called VMC and / or by air leaks existing between the room and the outside.
  • VMC ventilation device
  • this evacuated air is not evacuated with a sufficient flow rate to maintain the premises at a pressure close to atmospheric pressure and, under pain of seeing it be in a state of overpressure relative to the atmosphere, it is necessary to provide means for extracting this air.
  • the extraction means are generally brought together at the air plant where this air is treated, and from where it is then returned to the premises to be conditioned, by air ducts.
  • this procedure has several drawbacks.
  • suction means such as fans
  • additional ducts which increases the noise, the complexity, the size and the cost of the entire installation.
  • the air extracted from each of the rooms is returned, after passing through the central unit, to all the other rooms, which, from a hygienic or microbial point of view, especially when this type of installation is implemented in hospitals, hotels, or offices, presented significant health risks occupants of the premises concerned.
  • a main duct connected to the power plant supplies a series of air outlets arranged in parallel along this main pipeline.
  • the pressure drop between them can be significant, and thus the air flow rates blown into the corresponding premises can be very different.
  • this device has the drawback of generating vibrations and whistling at the level of the means intended to drop the pressure upstream of the blowing mouth.
  • the object of the present invention is to avoid the drawbacks mentioned above by proposing a particularly silent operating air conditioning device, since it makes it possible to reduce the two main noise generating factors of such an installation, namely the speed of the air. in contact with the walls of the ducts of ventilation of the device, and the speed of the air blown into the room to be conditioned, this air conditioning device also makes it possible to reduce the size of the ducts conveying the flow of air blown by the central unit and, consequently, , the size and the cost price of this type of installation.
  • the present invention thus relates to a device intended to regulate the temperature of a room by means of a low-speed air flow pulsed therein, comprising a suction mouth and a blowing mouth arranged in said room, the suction mouth and the blowing mouth opening into the same pipe in communication with a pipe for supplying air under pressure, by suction and blowing orifices, in which said pipe for supplying pressurized air opens at one end of said pipe, by at least one converging element from upstream to downstream, the suction and blowing outlets being respectively joined to the suction and blowing orifices by suction and blowing, characterized in that the most upstream part of the intersection surface between the suction duct and the pipe is disposed immediately downstream of the outlet orifice d e the converging element, so to create, in said pipe, between the suction and blowing orifices, two coaxial air streams, namely a central stream in which the air travels at high speed, and a peripheral air stream, surrounding the central air stream, in which air moves
  • the device according to the invention makes it possible, surprisingly, to reduce one of the main causes of the noise usually generated by this type of installation, namely the high flow velocity of the air flow on the internal surface of the sheath, since on the one hand the annular external vein behaves like a sound insulator and, on the other hand, this vein air moving at low speed relative to the wall, it causes minimal noise on the wall.
  • the central and annular air streams are created by having, in a blowing duct connected to an air conditioning unit, a converging element upstream downstream which creates, at the outlet, a central air stream at high speed and low pressure.
  • This central vein thus draws air into the room to be conditioned, which constitutes an annular vein surrounding the central vein, and which is driven at low speed by the latter. After a certain flow distance, depending on the operating parameters of the system, homogenization takes place in the flow channel and a homogeneous air flow is obtained, at low speed and at temperature equal to the temperature desired supply air, which is suitable for being blown into the room.
  • the Applicant has established that, in the field of air conditioning, effective homogenization is achieved when the distance separating the outlet orifice of the converging element from the mouth of blowing was at least seven times the diameter of the outlet of said converging element.
  • the present invention makes it possible to reduce both the noise and the temperature difference existing between the air blown into the room and the ambient air of this room, since the air coming from the plant, by mixing with the air extracted from the room, temperature drop, without however, the amount of calories or frigories it brings to the room does not decrease since all of the mixed air is forced into the room.
  • the present invention also makes it possible, with a noise lower than the devices of the prior art, to call upon an air flow coming from the power station which is at the same number of calories / frigories supplied, lower than that of the devices of the technique anterior.
  • the present invention makes it possible, with the same number of calories / frigories supplied, to reduce the temperature difference existing between the air blown into the room and the temperature of the latter, it allows, by increasing the temperature of the air supplied by the central unit, reducing the air flow required, and therefore the section of the supply duct.
  • the device according to the invention consists of an assembly consisting of a tubular element, which successively comprises from upstream to downstream, means for regulating the air streams coming from the power plant, a converging element from upstream to downstream, a first lateral orifice or air intake mouth, the part located most upstream is located in the vicinity of the outlet orifice of the converging element, and a second lateral orifice, or blowing mouth, located at a distance from said outlet orifice equal to at least seven times the diameter thereof, and means for closing off the end of the tubular element opposite the converging element.
  • This mode of implementation makes it possible to provide the user with an assembly ready to be installed on an installation, guaranteeing optimum efficiency, both in terms of noise level and that of thermal efficiency, since all the elements have have been calculated, checked and arranged by the manufacturer.
  • the means for regulating the air streams are associated with a thermal regulation battery making it possible to adjust the temperature of the flow of air blown into the converging element.
  • Figure 1 is a horizontal and longitudinal sectional view of a first embodiment of the present invention.
  • Figures 2 and 3 are partial horizontal and longitudinal sectional views of two alternative embodiments of the device according to the invention.
  • Figure 4 is a view, in partial horizontal and longitudinal section, of a device according to the prior art.
  • FIG. 5 is a view in horizontal and longitudinal section of a particular form of implementation of the invention, improving the device shown in FIG. 4.
  • Figures 6 and 7 are views in horizontal and partial longitudinal section, of two alternative embodiments of the device according to the invention.
  • Figure 8 is a horizontal and longitudinal sectional view of a compact assembly of the device according to the invention.
  • Figure 9 is a longitudinal sectional view of an alternative embodiment of a converging element.
  • FIG. 10 is a right view of the converging element shown in FIG. 9.
  • the device shown in FIG. 1 comprises a supply sheath 1, one end of which is in communication with an air conditioning unit (not shown in the drawing), and the opposite end ends in a convergent element 2, consisting of a frustoconical tube whose passage section decreases from upstream to downstream to form an outlet orifice 3 of diameter d , and which opens into a coaxial conduit 4 of which the diameter is equal to approximately twice the diameter d of the outlet orifice 3.
  • This duct 4 is connected by a sheath 6 to a blowing mouth 5 disposed in a partition 7 of a room 9 for which packaging is desired air.
  • a suction or "return” mouth 11 is connected to the conduit 4 by a transverse “recovery” sheath 13 which opens into the conduit 4 just downstream of the outlet orifice 3 of the converging element 2.
  • the axis zz ′ of the blowing mouth 5 is distant from the outlet orifice 3 of the converging element 2 of a length L equal to approximately 13 times the diameter d of the outlet orifice 3 of the converging element 2 .
  • the latter drives, at low speed, the air stream annular 17 which surrounds it, so that, in the present device, the air streams of the external vein 17, which are in contact with the walls of the duct 4, move at low speed and therefore only create one extremely low noise. It will also be noted that the reduction in noise is further improved by the fact that the annular air stream 17 behaves as a sound insulator with respect to all the noises conveyed by the central air stream 15.
  • the device according to the invention will reach its maximum efficiency only when the length L of the duct 4 is such that the central air stream 15, at high speed, does not encounter any obstacle, and the elbow 19 joining the duct 4 to the mouth of blowing 5 must therefore, in this embodiment, be located at a sufficient distance from the outlet orifice 3 of the converging element 2, so as not to be struck by the central air stream 15.
  • such distance L is at least equal to seven times the diameter d of the outlet orifice 3 of the converging element 2.
  • a closed space 20 can be provided, the depth of which is preferably equal to a quarter of the diameter of the duct 4, whose air it contains behaves like a pneumatic shock absorber pad.
  • the air flow q s pulsed therein, through the blowing mouth 5, is at a temperature T s .
  • This air flow q s consists, on the one hand, of a flow q l taken for example inside the room 9, and which is therefore at the temperature T and, on the other hand, of the flow q c at a temperature T c coming from the power station.
  • the induction coefficient ⁇ which is, by definition, the ratio of the air flow q l taken for example inside the room 9, over the total flow q s blown by the blowing mouth 5 in the room 9, and which can be varied, on the one hand by construction, and on the other hand by varying the pressure of the air supplied by the power plant to the device according to the invention, makes it possible to adapt the latter to the different conditions of work desired.
  • the device of the prior art requires, to be maintained at a constant temperature T of 20 ° C, an air flow at 50 ° C of 214m3 / hour, the air at 50 ° C thus blown into the room 9 will have a temperature difference of 30 ° C with the ambient temperature of 20 ° C of said room.
  • an induction coefficient ⁇ of 0.5 that is to say a flow of air q s blown into the room composed of 50% of air coming from the power station and from 50% of air sampled, in room 9
  • air is blown into it from the mixture of a flow q c of 214m3 / h at 50 ° C and a flow q l of 214m3 / h at 20 ° C, i.e. a flow q s of 428m3 / h of air at 35 ° C.
  • the temperature difference between the air blown into the room 9 and the ambient air thereof is 15 ° C., which is twice less than in the systems of the prior art.
  • the induction coefficient ⁇ will be increased. For example, with an induction coefficient of 0.67, if we take, for example, from the room, 67% of the air flow q s blown into it, we take from it 428m3 / h of air at 20 ° C which is mixed with 214m3 / h of air at 50 ° C coming from the power station, so as to blow into room 9 an air flow q s of 642m3 / h air at 30 ° C. The temperature of the air blown into room 9 therefore only exceeds the ambient temperature by 13 ° C.
  • the present invention also makes it possible to make use of an air flow q c coming from the power station which is, at the number of calories / frigories supplied equal, lower than that of the devices of the prior art.
  • the power plant can supply 134m3 / h of air at 80 ° C, which represents the same amount of calories supplied to the room.
  • an induction coefficient ⁇ of 0.60 which corresponds to a sampling in room 9 of 60% of the flow q s blown into it
  • the flow q s breaks down, as seen above, into , on the one hand, an air flow q c of 134m3 / h at 80 ° C supplied by the power plant and on the other hand an air flow q l of 200m3 / h at 20 ° C taken from room 9 , which corresponds to an overall air flow q s of 334m3 / h of air at 44 ° C.
  • the present invention can also be used in cooling mode, that is to say in summer, to maintain a room 9 at a constant temperature T, by blowing therein air from a central packing plant. air at a temperature T, below the ambient room temperature.
  • air at a temperature T below the ambient room temperature.
  • T 25 ° C
  • 32 ° C 25 ° C
  • the quantity of frigories thus provided is not sufficient, and the temperature of the blown air cannot be lowered down under pain of creating discomfort for the user of the room.
  • induction not only makes it possible to supply room 9 with the quantity of frigories necessary to ensure its temperature regulation, without requiring an increase in the cross section of the sheaths 1 or of the supply conduits 4, but also makes it possible blow air into them closer to the ambient temperature of room 9 which gives the user better comfort. It will be noted that, with an installation according to the prior art, to supply the same number of frigories to the room, under the same conditions of comfort, one should have pulsed therein a flow of 535m3 / h of air at 17 , 8 ° C.
  • FIG. 2 shows an assembly composed of a tubular element 40 on one end of which is connected a sheath 1 (in dashes) with an internal diameter D close to 200mm, connected to an air conditioning unit, and the other end of which is connected to another sheath 1 ′ (in dashes) of the same diameter D, connected to a blowing mouth, not shown in the drawing.
  • a cylindrical exchanger 42 is arranged at the inlet and inside of the tubular element 40.
  • the exchanger 42 is supplied with heat transfer fluid by two pipes 44 and 46.
  • This exchanger 42 is followed by a convergent element 2, the outlet orifice 3 of which is of substantially equal diameter d to one third of the internal diameter D of the sheaths 1.1 ′.
  • a transverse cylindrical tube 48 Immediately downstream of the outlet orifice 3, a transverse cylindrical tube 48, of the same diameter D as the sheaths 1,1 ′ opens into the tubular element 40.
  • exchangers 42 are usually used, combined with means making it possible to ensure good distribution of the air streams, which makes it possible to improve the homogeneity of the air speed inside the vein d air supplied to the converging element 2 and, consequently, that of the veins central 15 and annular 17, and finally, the soundproofing qualities of the device according to the invention.
  • the exchanger 42 of FIG. 2 has been replaced by a system for controlling the flow of air blown by the power station.
  • This system consists of two differential sensors 50,52 respectively disposed upstream and downstream of a convergent element 2, so as to benefit from the pressure drop created by it and which is necessary for this type of measurement.
  • the device comprises a register 54, housed in the tubular element 40, upstream of the converging element 2, movable in rotation about a transverse axis 56, and which makes it possible, depending on its angular position, to close more or less the tubular element 40, and servo means 58 able to control the register 54 according to the measurements of the sensors 50 and 52 and the operating conditions defined by the user.
  • the pressure drop created by the convergent element 2 to carry out the measurement, this therefore eliminates the elements, such as the braces, of the prior art.
  • an installation according to the prior art comprises a main sheath 1, of large section, which supplies a series of premises 9, each comprising a blowing mouth 5 joined, by a sheath 1 a , to a main supply sheath 1, the sheaths 1 a being mounted in parallel with one another on the main sheath 1. It is known that, in a conventional installation of this type, there is a pressure drop between the blowing mouth 5 located furthest upstream and the blowing loop 5 ′ situated furthest downstream, at a distance which, in the case of a very long sheath, can be significant .
  • the increase in the flow rate of the upstream blowing mouth 5 is thus 87%, and it can be seen, under these conditions, that the means to be used to bring this flow down to that of the downstream blowing mouth 5 ′ will be relatively large since the flow must be substantially divided by two.
  • FIG. 5 represents an installation of the same type, but implemented according to the present invention. It comprises a series of devices such as those represented in FIGS. 1 to 3 previously described, in which the supply and return pipes have diameters of the order of three times that of the outlet orifice 3 of the element converge 2, and the distances between the axes zz ′ of the air outlets 5 and the outlet orifices 3 of the converging elements 2 are of the order of 10 times the diameter of the latter. These devices are arranged in parallel on the main pipe 1, so as to blow, in a series of rooms 9, an air flow q s . As before, it will be assumed that the pressure drop existing between the upstream and downstream supply ducts is 50 pascals.
  • the device according to the invention plays a self-regulating role in flow, since the rate of increase in flow due to the same pressure drop, which was 87% in an installation according to the prior art, increases to a value of 10% in an installation according to the invention. This difference would be even more marked in the case of a longer supply sheath 1 and therefore having a higher pressure drop.
  • the rates of increase in the flow rate blown by the upstream mouth compared to that of the downstream mouth are respectively 144% for the following devices the prior art and 15% for the devices according to the invention.
  • converging element 2 composed of several trunks of coaxial cones.
  • FIG. 6 it is possible to use a converging element 2 consisting of an external converging element 2a and an internal converging element 2b, these two elements being linked by longitudinal spacers 22.
  • This arrangement makes it possible to limit the turbulence and obtaining more stable central and annular veins 17 and 17, which improves the soundproofing of the device according to the invention.
  • This arrangement therefore makes it possible, either at an equal sound level and at equal consumed energy, to increase the induction coefficient ⁇ , or at an equal induction coefficient ⁇ to decrease the sound level and the energy consumed.
  • the converging element 2 can consist of an eccentric truncated cone, that is to say of which the axis uu ′ of the outlet orifice 3 is offset laterally by a value a relative to the longitudinal axis yy ′ of the supply sheath 1.
  • This truncated cone is integral with a cylindrical part 62, of axis yy ′ fitting inside the sheath 1. This arrangement allows, by rotating the entire truncated cone and the cylindrical part 62 around the axis yy ′, to vary the induction coefficient ⁇ by moving the central air stream 15 more or less away from the outlet of the return sheath 13.
  • the device consists of an assembly comprising a tubular element 70 of longitudinal axis yy ′, open at its upstream end and closed at its downstream end.
  • This tubular element 70 receives, from upstream to downstream, a device 71 intended to regulate the flow of air coming from the power station, a convergent element 2, a rectangular suction mouth 72, with a long longitudinal axis.
  • suction 72 and blowing 74 vents are surrounded by a frame, respectively 73 and 76 provided with louvers 77, intended to ensure good orientation of the flows of aspirated and blown air.
  • the most upstream part of the suction mouth 72 is in alignment, along a transverse axis xx ′ perpendicular to the longitudinal axis yy ′, with the outlet orifice 3 of the converging element 2.
  • the axis uu ′ of the blowing mouth 76 is disposed at a distance from the outlet orifice 3 of the converging element 2 equal to substantially 13 times the diameter d of the outlet orifice 3 of the converging element 2.
  • Such an assembly includes all the elements of the device according to the invention arranged so as to provide a minimum operating noise associated with optimal operating qualities.
  • This assembly is intended to be fixed to the partition 9 of a room to be conditioned, without requiring calculations on the part of the installer due to its unitary design, which greatly facilitates its implementation and also constitutes a guarantee that the various elements of the device have been assembled in order to provide the best result.
  • the device 71 intended to ensure the regulation of the air flow in coming from the power plant, can be provided, in a known manner, with exchanger means supplied with heat transfer fluid by pipes, these exchanger means making it possible to adjust the quantity of calories / frigories coming from the power plant intended to be supplied to the system.
  • the Applicant has found that by using a converging element 2 having a wall of generally frustoconical shape, consisting of a series of adjacent undulations, an improvement in the stability of the air flow was obtained which further contributed to reduce device noise.
  • the converging element 2 consists, from upstream to downstream, of a cylindrical part 80, of an external diameter, preferably equal to the internal diameter D of the air supply duct 1 (shown in broken lines in the drawing), and of a second part 82, of overall shape in frusto-cone, consisting of a series of adjacent undulations 84, ending in a downstream outlet orifice 3 of average diameter d ′ corresponding to the diameter of the circle delimiting an internal surface equivalent to the surface of the outlet orifice 3 (shown in broken lines in FIG. 10).
  • the outlet orifice 3 of the converging element 2 thus has a periphery constituted of a succession of semicircles 85.
  • the corrugations 84 are of semi-frustoconical shape.
  • the diameter g of the large base and the diameter p of the small base of these semi-truncated cones are equal to one sixth respectively of the diameters D of the cylindrical part 80 and of the average diameter d ′ of the outlet orifice 3. This provision is particularly interesting in that it allows to increase the contact surface which improves the stability of the flow.

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Claims (16)

  1. Vorrichtung zur Temperaursteuerung eines Raumes mittels eines langsam in diesen gepulsten Luftstromes (qs), mit einer Lufteintrittsklappe (11, 72) und einer Luftaustrittsklappe (5, 74), welche in dem genannten Raum (9) angeordnet sind, wobei sowohl die Lufteintritts- (11,72) als auch die Luftaustrittsklappe (5, 74) durch Ansaug- und Abluftöffnungen in ein und dieselbe Rohrleitung (4) münden, welche mit einer unter Druck stehenden Luftzufuhrleitung (1) in Verbindung steht, bei der weiterhin die genannte unter Druck stehende Luftzufuhrleitung an einem Ende der genannten Rohrleitung (4) durch zumindest ein von oben in Richtung stromabwärts konvergentes Element (2) ausmündet, wobei die Lufteintritts- (11, 72) und die Luftaustrittsklappen (5, 74) jeweils durch einen Ansaug- (13) und einen Abluftkanal (6) mit den Ansaug- und Abluftöffnungen verbunden sind, dadurch gekennzeichnet, daß der am höchsten stomaufwärts befindliche Teil der Schnittfläche zwischen dem Ansaugkanal (13) und der Rohrleitung (4) unmittelbar stromabwärts der Auslaßöffnung (3) des konvergenten Elementes (2) so angeordnet ist, daß in der genannten Rohrleitung (4), zwischen der Ansaug- und der Abluftöffnung, zwei koaxiale Luftadern geschaffen werden, genauer gesagt eine zentrale Luftader (15), in welcher sich die Luft sehr schnell fortbewegt, und eine periphere Luftader (17), die die zentrale Luftader umgibt und in welcher sich die Luft nur langsam fortbewegt.
  2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die periphere Luftader (17) durch Verschieben der mittigen Luftader (15) auf Grund der durch die Lufteintrittsklappe (11, 72) in den Raum (9) angesaugten Luft geschaffen wird.
  3. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß die Achse (zz′) des Abluftkanales (6) in einer Entfernung (L) von der Auslaßöffnung (3) des konvergenten Elementes (2) angeordnet ist, die zumindest dem Siebenfachen des Durchmessers (d) der Auslaßöffnung (3) des genannten konvergenten Elementes (2) entspricht.
  4. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß der Durchmesser (D) der Rohrleitung (4), in welche das konvergente Element (2) mündet, zumindest gleich dem Zweifachen des Durchmessers (d) der Auslaßöffnung (3) des konvergenten Elementes (2) entspricht.
  5. Vorrichtung nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß sie Mittel zur Regelung des Durchsatzes des durch die Luftzufuhrleitnng (1) zugeführten Luftstromes aufweist.
  6. Vorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß das konvergente Element aus einem Kegelstumpf (2) besteht, dessen äußerer Durchmesser der großen Grundfläche mit dem inneren Durchmesser (D) des Kanales (1), welcher mit den unter Druck stehenden Luftzufuhrmitleln verbunden ist, übereinstimmt.
  7. Vorrichtung nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, daß das konvergente Element (2) aus zwei koaxialen Kegelstümpfen besteht, genauer gesagt aus einem ersten äußeren Kegelstumpf (2a) und einem zweiten inneren Kegelstumpf (2b), welcher auf dem ersten Kegelstumpf (2a) mit Hilfe von Radial- und Längsstreben (22) befestigt ist.
  8. Vorrichtung nach einem der Ansprüche 6 oder 7, dadurch gekennzeichnet, daß die Längsachse (uu′) der Auslaßöffnung (3) des konvergenten Elementes (2) gegenüber der Längsachse (yy′) des Zufuhrkanales (1) quer verschoben ist.
  9. Vorrichtung nach Anspruch 8, dadurch gekennzeichnet, daß das konvergente Element (2) aus einem Stück mit einem zylindrischen Grundkörper (62) gefertigt ist, welcher drehbeweglich um eine Achse (yy′) des Zufuhrkanales (1) gelagert ist.
  10. Vorrichtung nach einem der Ansprüche 1 bis 9, dadurch gekennzeichnet, daß stromaufwärts des konvergenten Elementes (2) ein Austauscher (42) angeordnet ist, mit Hilfe dessen die Temperatur des durch die Luftzufuhrleitung (1) zugeführten Luftstromes (qc) eingestellt werden kann.
  11. Vorrichtung nach einem der Ansprüche 1 bis 10, dadurch gekennzeichnet, daß stromaufwärts des konvergenten Elementes (2) Vorrichtungen angeordnet sind, mittels derer die Luftströme aus den unter Druck stehenden Luftzufuhrmitteln gesteuert werden können.
  12. Vorrichtung nach einem der Ansprüche 1 bis 11, dadurch gekennzeichnet, daß stromaufwärts des konvergenten Elementes (2) Vorrichtungen (54) angeordnet sind, die eine Einstellung des Durchsatzes des Luftstromes (qc) aus den unter Druck stehenden Luftzufuhrmitteln ermöglichen.
  13. Vorrichtung nach Anspruch 12, dadurch gekennzeichnet, daß auf beiden Seiten des konvergenten Elementes (2) Druckmeßwertgeber (50, 52) angeordnet sind, mit Hilfe derer der Durchsatz des aus dem konvergenten Element austretenden Luftstromes gemessen wird.
  14. Vorrichtung nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, daß das konvergente Element (2) von oben in Richtung stromabwärts aus einem ersten zylindrischen Teil (80) mit einem äußeren Durchmesser (D), der vorzugsweise dem inneren Durchmesser des Luftzufuhrkanales (1) entspricht, besteht sowie aus einem zweiten Teil (82), welches im wesentlichen die Form eines Kegelstumpfes aufweist und aus einer Reihe von Wellengebilden (84) besteht.
  15. Vorrichtung nach Anspruch 14, dadurch gekennzeichnet, daß die Wellengebilde (84) im wesentlichen eine kegelstumpfartige Form aufweisen, wobei die jeweiligen Durchmesser (g) und (p) der großen und der kleinen Basis der halbkegdstumpfartigen Wellengebilde (84) in etwa einem Sechstel der entsprechenden Durchmesser (D) des ersten zylindrischen Teiles (80) und des mittleren Durchmessers (d′) der Auslaßöffnung (3) des konvergenten Elementes (2) entsprechen.
  16. Vorrichtung nach einem der Ansprüche 1 bis 15, dadurch gekennzeichnet, daß die Rohrleitung (4) von oben in Richtung stromabwärts verlängert ist und zwar über die Austrittsöffnung hinaus durch einen geschlossenen Raum (20), dessen Tiefe (p) in etwa einem Viertel des Durchmessers der Rohrleitung (4) entspricht, so daß die in diesem enthaltene Luft wie ein pneumatischer Puffer wirkt.
EP92909650A 1991-04-08 1992-04-08 Vorrichtung zur raumtemperatursteuerung Expired - Lifetime EP0531508B1 (de)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
FR9104263 1991-04-08
FR9104263A FR2674943B1 (fr) 1991-04-08 1991-04-08 Dispositif de regulation en temperature d'un local.
PCT/FR1992/000312 WO1992017740A1 (fr) 1991-04-08 1992-04-08 Dispositif de regulation en temperature d'un local
US08/182,669 US5413530A (en) 1991-04-08 1994-01-14 Device for controlling temperature in a room

Publications (2)

Publication Number Publication Date
EP0531508A1 EP0531508A1 (de) 1993-03-17
EP0531508B1 true EP0531508B1 (de) 1995-03-15

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US (1) US5413530A (de)
EP (1) EP0531508B1 (de)
AT (1) ATE119989T1 (de)
ES (1) ES2072759T3 (de)
FR (1) FR2674943B1 (de)
WO (1) WO1992017740A1 (de)

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FI91319C (fi) * 1993-04-23 1994-06-10 Flaekt Oy Ilmastointilaitteiston tuloilman ja palautusilman välinen sekoitusosa
AUPN164695A0 (en) * 1995-03-10 1995-04-06 Luminis Pty Limited Improved induction nozzle and arrangement
CA2151773C (en) * 1995-06-14 2000-03-28 Vernon Casper Badry Air inductor device for controlled fresh air intake in an air heating system
FR2756366B1 (fr) 1996-11-28 1999-01-08 Spirec Dispositif reducteur de la pression de l'air fournie par une centrale de conditionnement d'air
FR2768803B1 (fr) 1997-09-19 1999-11-19 Spirec Perfectionnement aux dispositifs de controle et de regulation d'un flux d'air souffle dans un local
AU1866399A (en) * 1997-12-30 1999-07-26 Hydro-Quebec Integrated heating and fresh air supply device for use with an air distribution system
DE19806427A1 (de) * 1998-02-17 1999-08-19 Fleissner Maschf Gmbh Co Luftmischer zum statischen Vermischen von zwei Luftströmungen
FR2800854B1 (fr) * 1999-11-08 2002-01-04 Diffusion Thermique Ouest Sa Systeme de diffusion d'air
CA2304406A1 (fr) 2000-04-04 2001-10-04 Hydro-Quebec Unite de chauffage diffusion encastrable
FR2870326B1 (fr) 2004-05-14 2006-07-28 France Air Installation pour le chauffage, le rafraichissement et la ventilation de logements collectifs
US8336672B2 (en) * 2006-01-18 2012-12-25 Bard Manufacturing Company Air treatment and sound reduction system
FR2916261B1 (fr) * 2007-05-18 2010-03-12 Alain Katz Systeme de diffusion d'air dans une enceinte
FR2962525B1 (fr) * 2010-07-06 2014-08-29 Goetinck Herve Jean Dispositif de conditionnement d'air pour prevenir, a basse temperature exterieure, l'apparition de givre sur les pompes a chaleur, et pour ameliorer leur fonctionnement a temperature exterieure elevee
US20120190290A1 (en) * 2011-01-20 2012-07-26 Shahriar Nick Niakan Air intake flow device and system
CZ2018531A3 (cs) * 2018-10-05 2019-12-11 Prihoda Sro Vzduchotechnický pomocný potrubní dílec a vzduchotechnické potrubí
FR3090827B1 (fr) * 2018-12-19 2021-05-28 Ludovic Boulanger Gaine d’aeration

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DE3044080A1 (de) * 1980-11-24 1982-09-09 Schmidt Reuter Ingenieurgesellschaft mbH & Co KG, 5000 Köln Raumlufttechnische anlage
FR2656071A1 (fr) * 1989-12-20 1991-06-21 Montaz Edmond Dispositif de regulation en temperature d'un local.

Also Published As

Publication number Publication date
ATE119989T1 (de) 1995-04-15
WO1992017740A1 (fr) 1992-10-15
EP0531508A1 (de) 1993-03-17
US5413530A (en) 1995-05-09
FR2674943B1 (fr) 1996-02-09
FR2674943A1 (fr) 1992-10-09
ES2072759T3 (es) 1995-07-16

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