CA1324021C - Method and apparatus for the air conditioning of rooms - Google Patents
Method and apparatus for the air conditioning of roomsInfo
- Publication number
- CA1324021C CA1324021C CA000551165A CA551165A CA1324021C CA 1324021 C CA1324021 C CA 1324021C CA 000551165 A CA000551165 A CA 000551165A CA 551165 A CA551165 A CA 551165A CA 1324021 C CA1324021 C CA 1324021C
- Authority
- CA
- Canada
- Prior art keywords
- room
- air
- fresh air
- ceiling
- heat exchanger
- 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 - Fee Related
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Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F7/00—Ventilation
- F24F7/04—Ventilation with ducting systems, e.g. by double walls; with natural circulation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
- F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
- F24F11/76—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity by means responsive to temperature, e.g. bimetal springs
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Central Air Conditioning (AREA)
- Duct Arrangements (AREA)
Abstract
ABSTRACT
The room air conditioning method provides for a regulation or control of the fresh air volume supplied to the room and the removal of spent internal air from the upper room air layers.
At least approximately room-isothermal fresh air is introduced in laminar manner into the room from the ceiling area. The flow rate of the introduced fresh air assists the formation of room inherent dynamic partial flows. The fresh air in the ceiling area is preferably supplied in the vicinity of room inner walls facing front walls. A volume flow regulator is controlled in accordance with a temperature measurement on the laminar diffuser. A heat exchanger is preferably connected to the fresh air duct in the ceiling area and is followed by a diffuser . The fresh air brought almost to room temperature in the heat exchanger is passed from top to bottom and directed in a substantially laminar manner into the room. Through temperature adaptation of the room air with the aid of fresh air in the heat exchanger and the supply of isothermal fresh air with a low flow rate into the room, the comfort characteristics of the air conditioning apparatus are decisively improved.
The room air conditioning method provides for a regulation or control of the fresh air volume supplied to the room and the removal of spent internal air from the upper room air layers.
At least approximately room-isothermal fresh air is introduced in laminar manner into the room from the ceiling area. The flow rate of the introduced fresh air assists the formation of room inherent dynamic partial flows. The fresh air in the ceiling area is preferably supplied in the vicinity of room inner walls facing front walls. A volume flow regulator is controlled in accordance with a temperature measurement on the laminar diffuser. A heat exchanger is preferably connected to the fresh air duct in the ceiling area and is followed by a diffuser . The fresh air brought almost to room temperature in the heat exchanger is passed from top to bottom and directed in a substantially laminar manner into the room. Through temperature adaptation of the room air with the aid of fresh air in the heat exchanger and the supply of isothermal fresh air with a low flow rate into the room, the comfort characteristics of the air conditioning apparatus are decisively improved.
Description
METIIOD ~D APP~RATUS FO~ TIIE AIR CONDITIONING OF ROOMS
The invention relates to a method for the air conditioning of rooms or spaces in accordance with the preamble of claim 1, as well as to an air conditioning apparatus for performing the method having a volume-regulated fresh air duct, an air exchanger and a spent air duct.
Room air conditioning installations are intended to keep the room temperature at a uniform value, which is considered to be comforta~le, whilst also ensuring a fresh air supply. The air conditioning installation must be in a position to compensate varyingly pronounced temperature changes in the rooms through the most varied heat sources or heat losses. The heat sources which heat the room during the period of use are on the one hand constituted by equipment or machines and on the other by the persons located in the rooms. An important part in the heat balance of the individual rooms is also played by heat received, e.g. through glazed window surfaces.
A regulated air exchange is used for reducing the thermal excesses produced by such varied sources. In order that the regulating or control process can take place under clearly defined conditions, windows must be kept closed in such buildings. Therefore it is also necessary to provide a fresh air supply and integrated into the system, so that spont and in part contaminated room air can be regularly replaced.
!
Known room air conditioning installations e.g. contain a fresh air duct which, compared with the room air, leads cool fresh air directly into the room. The fresh air has a temperature difference of several C compared with the room air. A
quantity or volums regulator, e.g. a valve flap is provided in the intake zone to the air conditioned rooms. Spent air is j returned from the room via a spent air duct. For special purposes, e.g. in operating theatres, there are also laminar air exchangers or diffusers. In this case, considerable - quantities of air are passed via large-area diffusers into the room, so that there is a large air quantity exchange without taking account of the inherent dynamic characteristics 132~021 of tl~e room. Ilitherto diffusers with a laminar air discharge have not been used in general room air conditioning.
According to the state of the art fresh air is broken down into individual jets and, as stated, blown at high speed and with a relatively high temperature difference compared with the room air into the said room. This pronounced air jet must mix at a very limited distance with the room air in order to assume the desired mixture temperature. The air volume in such a room is circu]ated with a high intensity, which leads to a highly turbulent room air flow. These phenomena are the reason why known air conditioning equipment in rooms, where persons spend a long time at the same place, e.g. sitting at work, are frequently considered to be unpleasant. Tl-e reasons given are draughts and noise as a result of the inflowing and/or outflowing air. This constitutes a reason for the relatively frequent refusal to install air conditioning installations.
However, it has been found that air conditioning installations are desirable from other standpoints, particularly in offices and shops.
The problem of the present invention is to provide a method and an apparatus for the air conditioning of rooms or spaces, or to so improve existing methods and apparatuses that a significant improvement is achieved in the degree of comfort, whilst also having both lower energy requirements and lower constructional costs compared with the known installations.
According to the invention this problem is solved by a method according to claim 1 and an air~conditioning apparatus according to claim 7.
Such a method and such an apparatus have important, significant advantages compared with the known installations. Firstly the comfort characteristics of the air conditioning installation 1324~21 are decisively improved in that they are hardly noticed by persons in the room, let alone being considered disadvantageous.
This is a consequence of the supply of isothermal fresh air with an only limited flow speed into the room. Spent, heated room air automatically rises in the room and is removed at this high level. If higher temperature adaptations are required, a heat exchanger is connected upstream of the diffuser located in the ceiling area, so that the fresh air passinS out of the di~fuser into the room in this case has alreadly largely compensated its original temperature gradient compared with the room air in the heat exchanger. The fresh air entering the room consequently does not have a cooling or heating action. This air is used almost exclusively for fresh air supply purposes and is fed laterally from above and in laminar mamler into the room via the diffuser. The air is then distributed in accordance with the inherent dynamics of the room, i.e. in accordance with the existing and possibly changing circumstances, this taking place in an automatic manner and without any marked and therefore disturbing air flows.
Due to the smaller quantities of air supplied and removed, smaller cross-sections are required for the supply lines, which leads to space and cost savings. As a result of the division of functions, there is a much better overall energy requirement, which is e.g. only approximately 40% of that of conventional installations under otherwise identical conditions.
Another advantage of the quiet air flow in the room is the much greater purity of the room air. The contamination of the room air as a result of turbulence and high flow rates is reduced.
As the fresh air supply to the room now only takes place on one side at a greatly reduced speed, instead of at several points l~ith a high spoed whicll can be noticed by the room 1324~21 1l occupant, there is a much higher degree of freedom with regards to thc cquippillg and furnishing o~ the rooms.
Finally, through the use of a direct heat exchanger constructed as a ceiling element, it is possible to save on the overall height, because there is no need for separate air ducts in the ceiling area and therefore an additional suspended or hung ceiling. As no double floors are required for the air concl;tioJIins illsta]]ation, this air can bo ]~ept fr~ r necessary, for other installations, e.g. exclusively for electrical installations. As a result of the limited overall height of the installation, it is possible to adopt a lower room height in the buildings, which in the case of considerable building heights leads to significant improvements in the utilization of the building space and in extreme cases additional floors can be introduced within a given overall height.
The regulation or control of the fresh air volume preferably takes place by temperature measurements in the vicinity of the diffuser. The diffuser is generally located in the vicinity of the volume regulator, so that the installation is simple and inexpensive. There is no need for separate room thermostats or other sensors within the air conditioned room.
Additional features and advantages of the invention can be gathered from the following description.
The invention is described in greater detail hereinafter relative to preferred embodiment~ and with reference to the attached drawings, wherein show:
~ig. 1 A diagrammatic view of a room to be air conditioned with the main components of the inventive room air conditioning apparatus.
, Fig. 2 A plan view of the room according to fig. 1 ; with the arrangement of a heat exchangor in the ceiling area.
1324~21 ~ig. 3 S~ction 3-3 fronn fig. 2.
Fig. ~I The embodiment of a bypass-regulated heating system.
According to the represented exemplified embodiment, the air conditioning installation or apparatus is connected to a fresh air duct 1 and a spent air duct 2, a volurne regulator 3 being arrallse(l in ~hc fornlcr. Tho frosh air duct 1 ~nd s~en-t ~ir duct 2 are covered by a ceiling ~. It is also possible to provide in the room to be air conditioned a heat exchanger 5, which in the present embodiment is constructed as a ceiling element. If only limited temperature adaptations are necessary, there is no need for a separate heat exchanger.
As is shown in detail in fig. 2, the fresh air duct 1 is in this case directly connected to the forward fins 5A of the heat exchanger, which pass at the other end thereof into return fins 5B. The outlets from the return fins 5B lead in parallel to a diffuser 6, which passes in laminar flow manner into the room the fresh air from the ceiling, which is directed downwards as indicated by arrows A. Preferably diffuser 6 is arranged on one side of the room, which faces a window or front wall 7 thereof. In larger rooms the diffuser is preferably located in areas close to passages, i.e. not above working or waiting areas.
.
Fig. 3 shows the arrangement of the heat exchanger, constructed as a ceiling member, on the room ceiling 8. It is possible to see the construction of the forward fins 5A and the return fins 5B as rectangular tubes and their alternate arrangement directly on the room ceiling 8. Through the geometry and dimensioning of the heat exchanger fans acting as static cooling elements, an average surface temperature of the ceiling is set, which is roughly the same as the average room temperature.
In the case of very high heat exchange loads, the efficiency of the cooling fins can be increased by enlarging the free surfaces within the duct.
1~2402~
- G -As S]10~ llc risht-hand part of fig. 3, for so-called high performance zones the forward fins 5A and return fins 5B are provided with small air exchange openings, e.g. with slits 9, which speed up the heat exchange process between the fin wall and thc room air surrounding the fin in the vicinity of the heat exchanger. There is never a direct fresh air supply into the working or waiting area of the room at this point. In fact, there ;s a type of microflow exclusively in the surface area of the fins, which improves the efficiency of heat exchanger 6.
The fresh air fed from the fresh air duct 1, via volume regulator 3 into the forward fins 5A of heat exchanger 5 loses part of its temperature gradient compared with the room air via the heat exchanger fins, which are preferably made from metal or some other good heat conducting material. Further thermal potential is transferred from the fresh air via the heat exchanger to the room air on its return travel over the return fins 5B. At the outlet from the return fins 5B, the fresh air almost adapted to the room air temperature in the aforementioned manner is fed via diffuser 6 into the room.
The fresh air passing from the diffuser into the room must differ by a maximum of approximately 1C from the room temperature in the working area. The speed at which the fresh air is discharged from the diffuser is approximately 0.15 m/sec.
It is therefore much lower than the discharge speed of the fresh air fed into the room in conventional air conditioning installations, where it is approximately 1 to 3 m/sec.
The fresh air flowing out of the diffuser 6 flows downwards into the room, where it provides a fresh air supply. As a result of the various heat sources distributed over the room, the fresh air flows horizontally to the heat sources and, heated by the latter, vertically up to the ceiling, where it flows along the ceiling elements to an outlet 10, which passes into the spent air duct 2.
An upwardly directed hot air flow leads to a supply air flow, ~24021 which ;s branched directly laterally from the fresh air flowing out of diffuser 6. This leads to greater flow rolls, which cause virtually no turbulence and instead evolve inherent dynamics in the room, so that main flows present in the room are assisted. Such main flows are the fresh air flowing downwards from diffuser 6, branches to the various heat sources, the fresh air flow directed towards the front wall side, the upwardly flow in the front wall area aided by natural heating via the windows and the return flow in the ceiling area along heat exchanger 5 to the room air outlet 10. Despite the substantially laminar fresh air introduction into the room, there is a very good air exchange within the entire room.
This can mainly be attributed to the described measures with respect to an optimum utilization of the inherent dynamics of the room.
Air conditioning can take place both in the sense of a cooling and a heating of the room, or in quasi-isothermal operation for ventilation purposes. Particularly when heating, it can be appropriate to supply separate hot air and fresh air flows to the system and to carry out a regulated air mixing thereof in the diffuser area. As indicated in fig. 4, mixing takes place in a bypass 20 to heat exchanger 5. ~resh air at a low temperature, of e.g. 12C is directly supplied to the bypass.
Over heat exchanger 5 is fed air at e.g. 38C. In diffuser 6, there is a controlled mixing to 21 C, so that a room temperature of 22C is obtained.- This regulation or control takes place by means of a control valve 21 in bypass 20, a temperature sensor 22 in the vicinity of diffuser 6 cooperating with a regula'cing device 23 and switches the motor 24 of control valve 21 in a temperature-dependent manner.
The combination of static cooling surfaces on heat exchanger 5 and a laminar air inflow via diffuser 6, as well as the utilization of the inher-ent dynamics for the fresh air supply of the room lead to a low room air speed comparable to that of a non-air conditioned room, as well as a uniform room air temperature distribution in the working area. The apparatus ~32402~
~3 opcrates with an extremely low noise level and can be used even in the case of high thermal loads, particularly if the heat exchanger fins are provided with the aforementioned microopenings 9 for improving the heat exchange. Additional ducts or installation lines are not required within the room. The height of the heat exchanger fins is in a typical example approximately 15 cm, so that the normal room height for the non-air con(lit;oncd rooms can bo rctained substantialJy unchanged. Thus, no double ceilings are required, which make it necessary to have additional room height in conventional air conditioning installations. As a result of the inherent dynamic room air flow, which essentially takes place from bottom to top, whilst substantially avoiding any cross-flow with contaminated air, the level of pollutants within the room air is kept extremely low.
The regulation of the fresh air supply by means of volume regulator 3 takes place with a view to a constant exit temperature in diffuser 6. According to a preferred embodiment, the temperature of the primary air, i.e. the fresh air supplied in fresh air duct l is +12 C, whilst the spent air in spent air duct 2 has a temperature of +27C, the room temperature being +24C. The temperature difference between the primary air and the spent air is consequently 15C in this case. ~lowever~ in the known air conditioning installations with a direct introduction of cooled fresh air into the room, there is a temperature difference of max 8 to 10C, which leads to a greater air turbulence and therefore to a higher flow rate in the working area, whish leads to unpleasant, disturbing side-effects.
The desired exit temperature and therefore room temperature is achieved through an automatic volume flow adaptation, i.e.
by a temperature-volume cascade control. The system-controlling thermometer, optionally with a transducer, is integrated into the laminar flow diffuser 6. The regulating or control system operates according to the principle of a variable volume flow system VVS.
Through the direct arrangement of heat exchanger 5 on the building-side ceiling 8, e.g. using assembly rails 13 according to fig. 3, the ceiling with its heat storage capacity can be directly incorporated into the heat exchange system. This exercises an additional stabilizing effect on the overall systcm a~ s rcgulating systcm and increascs thc hcat exchange efficiency.
As a mo~ification to the described preferred embodiment, the heat exchanger can also be positioned at other suitable points within the room. Here again it is important that the fresh air supplied via the fresh air duct 1 initially passes through the heat exchanger and only then, after it has been virtually heated to room temperature, is it introduced into the room.
Although a good heat ronducting material, e.g. a metal suggests itself for the material used for heat exchanger 5, it can also be made from other materials, e.g. plastic.
The use of such an air conditioning apparatus is not restricted to the aforementioned offices and shops. The described apparatus can be advantageously used in testing laboratories or production rooms, where it is necessary to have balanced climatic conditions and in particular constant temperatures.
! ~
The invention relates to a method for the air conditioning of rooms or spaces in accordance with the preamble of claim 1, as well as to an air conditioning apparatus for performing the method having a volume-regulated fresh air duct, an air exchanger and a spent air duct.
Room air conditioning installations are intended to keep the room temperature at a uniform value, which is considered to be comforta~le, whilst also ensuring a fresh air supply. The air conditioning installation must be in a position to compensate varyingly pronounced temperature changes in the rooms through the most varied heat sources or heat losses. The heat sources which heat the room during the period of use are on the one hand constituted by equipment or machines and on the other by the persons located in the rooms. An important part in the heat balance of the individual rooms is also played by heat received, e.g. through glazed window surfaces.
A regulated air exchange is used for reducing the thermal excesses produced by such varied sources. In order that the regulating or control process can take place under clearly defined conditions, windows must be kept closed in such buildings. Therefore it is also necessary to provide a fresh air supply and integrated into the system, so that spont and in part contaminated room air can be regularly replaced.
!
Known room air conditioning installations e.g. contain a fresh air duct which, compared with the room air, leads cool fresh air directly into the room. The fresh air has a temperature difference of several C compared with the room air. A
quantity or volums regulator, e.g. a valve flap is provided in the intake zone to the air conditioned rooms. Spent air is j returned from the room via a spent air duct. For special purposes, e.g. in operating theatres, there are also laminar air exchangers or diffusers. In this case, considerable - quantities of air are passed via large-area diffusers into the room, so that there is a large air quantity exchange without taking account of the inherent dynamic characteristics 132~021 of tl~e room. Ilitherto diffusers with a laminar air discharge have not been used in general room air conditioning.
According to the state of the art fresh air is broken down into individual jets and, as stated, blown at high speed and with a relatively high temperature difference compared with the room air into the said room. This pronounced air jet must mix at a very limited distance with the room air in order to assume the desired mixture temperature. The air volume in such a room is circu]ated with a high intensity, which leads to a highly turbulent room air flow. These phenomena are the reason why known air conditioning equipment in rooms, where persons spend a long time at the same place, e.g. sitting at work, are frequently considered to be unpleasant. Tl-e reasons given are draughts and noise as a result of the inflowing and/or outflowing air. This constitutes a reason for the relatively frequent refusal to install air conditioning installations.
However, it has been found that air conditioning installations are desirable from other standpoints, particularly in offices and shops.
The problem of the present invention is to provide a method and an apparatus for the air conditioning of rooms or spaces, or to so improve existing methods and apparatuses that a significant improvement is achieved in the degree of comfort, whilst also having both lower energy requirements and lower constructional costs compared with the known installations.
According to the invention this problem is solved by a method according to claim 1 and an air~conditioning apparatus according to claim 7.
Such a method and such an apparatus have important, significant advantages compared with the known installations. Firstly the comfort characteristics of the air conditioning installation 1324~21 are decisively improved in that they are hardly noticed by persons in the room, let alone being considered disadvantageous.
This is a consequence of the supply of isothermal fresh air with an only limited flow speed into the room. Spent, heated room air automatically rises in the room and is removed at this high level. If higher temperature adaptations are required, a heat exchanger is connected upstream of the diffuser located in the ceiling area, so that the fresh air passinS out of the di~fuser into the room in this case has alreadly largely compensated its original temperature gradient compared with the room air in the heat exchanger. The fresh air entering the room consequently does not have a cooling or heating action. This air is used almost exclusively for fresh air supply purposes and is fed laterally from above and in laminar mamler into the room via the diffuser. The air is then distributed in accordance with the inherent dynamics of the room, i.e. in accordance with the existing and possibly changing circumstances, this taking place in an automatic manner and without any marked and therefore disturbing air flows.
Due to the smaller quantities of air supplied and removed, smaller cross-sections are required for the supply lines, which leads to space and cost savings. As a result of the division of functions, there is a much better overall energy requirement, which is e.g. only approximately 40% of that of conventional installations under otherwise identical conditions.
Another advantage of the quiet air flow in the room is the much greater purity of the room air. The contamination of the room air as a result of turbulence and high flow rates is reduced.
As the fresh air supply to the room now only takes place on one side at a greatly reduced speed, instead of at several points l~ith a high spoed whicll can be noticed by the room 1324~21 1l occupant, there is a much higher degree of freedom with regards to thc cquippillg and furnishing o~ the rooms.
Finally, through the use of a direct heat exchanger constructed as a ceiling element, it is possible to save on the overall height, because there is no need for separate air ducts in the ceiling area and therefore an additional suspended or hung ceiling. As no double floors are required for the air concl;tioJIins illsta]]ation, this air can bo ]~ept fr~ r necessary, for other installations, e.g. exclusively for electrical installations. As a result of the limited overall height of the installation, it is possible to adopt a lower room height in the buildings, which in the case of considerable building heights leads to significant improvements in the utilization of the building space and in extreme cases additional floors can be introduced within a given overall height.
The regulation or control of the fresh air volume preferably takes place by temperature measurements in the vicinity of the diffuser. The diffuser is generally located in the vicinity of the volume regulator, so that the installation is simple and inexpensive. There is no need for separate room thermostats or other sensors within the air conditioned room.
Additional features and advantages of the invention can be gathered from the following description.
The invention is described in greater detail hereinafter relative to preferred embodiment~ and with reference to the attached drawings, wherein show:
~ig. 1 A diagrammatic view of a room to be air conditioned with the main components of the inventive room air conditioning apparatus.
, Fig. 2 A plan view of the room according to fig. 1 ; with the arrangement of a heat exchangor in the ceiling area.
1324~21 ~ig. 3 S~ction 3-3 fronn fig. 2.
Fig. ~I The embodiment of a bypass-regulated heating system.
According to the represented exemplified embodiment, the air conditioning installation or apparatus is connected to a fresh air duct 1 and a spent air duct 2, a volurne regulator 3 being arrallse(l in ~hc fornlcr. Tho frosh air duct 1 ~nd s~en-t ~ir duct 2 are covered by a ceiling ~. It is also possible to provide in the room to be air conditioned a heat exchanger 5, which in the present embodiment is constructed as a ceiling element. If only limited temperature adaptations are necessary, there is no need for a separate heat exchanger.
As is shown in detail in fig. 2, the fresh air duct 1 is in this case directly connected to the forward fins 5A of the heat exchanger, which pass at the other end thereof into return fins 5B. The outlets from the return fins 5B lead in parallel to a diffuser 6, which passes in laminar flow manner into the room the fresh air from the ceiling, which is directed downwards as indicated by arrows A. Preferably diffuser 6 is arranged on one side of the room, which faces a window or front wall 7 thereof. In larger rooms the diffuser is preferably located in areas close to passages, i.e. not above working or waiting areas.
.
Fig. 3 shows the arrangement of the heat exchanger, constructed as a ceiling member, on the room ceiling 8. It is possible to see the construction of the forward fins 5A and the return fins 5B as rectangular tubes and their alternate arrangement directly on the room ceiling 8. Through the geometry and dimensioning of the heat exchanger fans acting as static cooling elements, an average surface temperature of the ceiling is set, which is roughly the same as the average room temperature.
In the case of very high heat exchange loads, the efficiency of the cooling fins can be increased by enlarging the free surfaces within the duct.
1~2402~
- G -As S]10~ llc risht-hand part of fig. 3, for so-called high performance zones the forward fins 5A and return fins 5B are provided with small air exchange openings, e.g. with slits 9, which speed up the heat exchange process between the fin wall and thc room air surrounding the fin in the vicinity of the heat exchanger. There is never a direct fresh air supply into the working or waiting area of the room at this point. In fact, there ;s a type of microflow exclusively in the surface area of the fins, which improves the efficiency of heat exchanger 6.
The fresh air fed from the fresh air duct 1, via volume regulator 3 into the forward fins 5A of heat exchanger 5 loses part of its temperature gradient compared with the room air via the heat exchanger fins, which are preferably made from metal or some other good heat conducting material. Further thermal potential is transferred from the fresh air via the heat exchanger to the room air on its return travel over the return fins 5B. At the outlet from the return fins 5B, the fresh air almost adapted to the room air temperature in the aforementioned manner is fed via diffuser 6 into the room.
The fresh air passing from the diffuser into the room must differ by a maximum of approximately 1C from the room temperature in the working area. The speed at which the fresh air is discharged from the diffuser is approximately 0.15 m/sec.
It is therefore much lower than the discharge speed of the fresh air fed into the room in conventional air conditioning installations, where it is approximately 1 to 3 m/sec.
The fresh air flowing out of the diffuser 6 flows downwards into the room, where it provides a fresh air supply. As a result of the various heat sources distributed over the room, the fresh air flows horizontally to the heat sources and, heated by the latter, vertically up to the ceiling, where it flows along the ceiling elements to an outlet 10, which passes into the spent air duct 2.
An upwardly directed hot air flow leads to a supply air flow, ~24021 which ;s branched directly laterally from the fresh air flowing out of diffuser 6. This leads to greater flow rolls, which cause virtually no turbulence and instead evolve inherent dynamics in the room, so that main flows present in the room are assisted. Such main flows are the fresh air flowing downwards from diffuser 6, branches to the various heat sources, the fresh air flow directed towards the front wall side, the upwardly flow in the front wall area aided by natural heating via the windows and the return flow in the ceiling area along heat exchanger 5 to the room air outlet 10. Despite the substantially laminar fresh air introduction into the room, there is a very good air exchange within the entire room.
This can mainly be attributed to the described measures with respect to an optimum utilization of the inherent dynamics of the room.
Air conditioning can take place both in the sense of a cooling and a heating of the room, or in quasi-isothermal operation for ventilation purposes. Particularly when heating, it can be appropriate to supply separate hot air and fresh air flows to the system and to carry out a regulated air mixing thereof in the diffuser area. As indicated in fig. 4, mixing takes place in a bypass 20 to heat exchanger 5. ~resh air at a low temperature, of e.g. 12C is directly supplied to the bypass.
Over heat exchanger 5 is fed air at e.g. 38C. In diffuser 6, there is a controlled mixing to 21 C, so that a room temperature of 22C is obtained.- This regulation or control takes place by means of a control valve 21 in bypass 20, a temperature sensor 22 in the vicinity of diffuser 6 cooperating with a regula'cing device 23 and switches the motor 24 of control valve 21 in a temperature-dependent manner.
The combination of static cooling surfaces on heat exchanger 5 and a laminar air inflow via diffuser 6, as well as the utilization of the inher-ent dynamics for the fresh air supply of the room lead to a low room air speed comparable to that of a non-air conditioned room, as well as a uniform room air temperature distribution in the working area. The apparatus ~32402~
~3 opcrates with an extremely low noise level and can be used even in the case of high thermal loads, particularly if the heat exchanger fins are provided with the aforementioned microopenings 9 for improving the heat exchange. Additional ducts or installation lines are not required within the room. The height of the heat exchanger fins is in a typical example approximately 15 cm, so that the normal room height for the non-air con(lit;oncd rooms can bo rctained substantialJy unchanged. Thus, no double ceilings are required, which make it necessary to have additional room height in conventional air conditioning installations. As a result of the inherent dynamic room air flow, which essentially takes place from bottom to top, whilst substantially avoiding any cross-flow with contaminated air, the level of pollutants within the room air is kept extremely low.
The regulation of the fresh air supply by means of volume regulator 3 takes place with a view to a constant exit temperature in diffuser 6. According to a preferred embodiment, the temperature of the primary air, i.e. the fresh air supplied in fresh air duct l is +12 C, whilst the spent air in spent air duct 2 has a temperature of +27C, the room temperature being +24C. The temperature difference between the primary air and the spent air is consequently 15C in this case. ~lowever~ in the known air conditioning installations with a direct introduction of cooled fresh air into the room, there is a temperature difference of max 8 to 10C, which leads to a greater air turbulence and therefore to a higher flow rate in the working area, whish leads to unpleasant, disturbing side-effects.
The desired exit temperature and therefore room temperature is achieved through an automatic volume flow adaptation, i.e.
by a temperature-volume cascade control. The system-controlling thermometer, optionally with a transducer, is integrated into the laminar flow diffuser 6. The regulating or control system operates according to the principle of a variable volume flow system VVS.
Through the direct arrangement of heat exchanger 5 on the building-side ceiling 8, e.g. using assembly rails 13 according to fig. 3, the ceiling with its heat storage capacity can be directly incorporated into the heat exchange system. This exercises an additional stabilizing effect on the overall systcm a~ s rcgulating systcm and increascs thc hcat exchange efficiency.
As a mo~ification to the described preferred embodiment, the heat exchanger can also be positioned at other suitable points within the room. Here again it is important that the fresh air supplied via the fresh air duct 1 initially passes through the heat exchanger and only then, after it has been virtually heated to room temperature, is it introduced into the room.
Although a good heat ronducting material, e.g. a metal suggests itself for the material used for heat exchanger 5, it can also be made from other materials, e.g. plastic.
The use of such an air conditioning apparatus is not restricted to the aforementioned offices and shops. The described apparatus can be advantageously used in testing laboratories or production rooms, where it is necessary to have balanced climatic conditions and in particular constant temperatures.
! ~
Claims (14)
1. Method for room air conditioning by regulating the fresh air volume supplied to the room and removal of spent air from the upper room air layers, characterized by a laminar introduction of at least approximately room-isothermal fresh air from a clearly defined ceiling area, with a flow rate, which assists the formation of room inherent dynamic partial flows corresponding to the various heat sources present in the room.
2. Method according to claim 1, characterized in that the fresh air is supplied in the ceiling area in the vicinity of the room inner walls facing front walls.
3. Method according to claim 1, characterized in that the fresh air is supplied in ceiling areas close to passages.
4. Method according to claim 1, characterized in that in accordance with the rules of variable volume flow systems, the maximum volume flow is regulated in accordance with the maximum expected temperature compensating load of the room, that the minimum fresh air volume flow is regulated according to the air hygienic conditions in the room and that the temperature guidance for the volume flow regulator is carried out from the region of the laminar diffuser.
5. Method according to claim 4, characterized in that on reaching the minimum volume flow and reduced thermal load of the room, there is a temperature rise for the minimum volume flow in a sequential control.
6. Method according to claim 4, characterized in that the volume flow regulator is set to a maximum limitation for the fresh air exit speed from the laminar diffuser 6 of max 0.15 m/sec.
7. Air conditioning apparatus for performing the method according to claim 1 with volume-regulated fresh air duct, with an air outlet and with a spent air duct, characterized in that a heat exchanger (5) is connected to the fresh air duct (1) in the ceiling area, that a diffuser (6) is connected downstream of the heat exchanger and from which the fresh air almost brought to room temperature in the heat exchanger is directed from top to bottom in substantially laminar manner into the room, the room air in the upper area of the room passing along the heat exchanger (5) and is subsequently passed into the spent air outlet (10) located in the ceiling area.
8. Apparatus according to claim 7, characterized in that fin-like ceiling members are used as heat exchangers (5) and comprise parallel, alternating forward fins (5A) and return fins (5B), the forward fins being jointly connected to the fresh air duct (1) and the return fins jointly pass into diffuser (6).
9. Apparatus according to claim 7, characterized in that a fresh air bypass (20) is associated with heat exchanger (5) and issues together with the latter into diffuser (6).
10. Apparatus according to claim 9, characterized in that the fresh air bypass (20) is provided with a regulated valve (21), the associated regulator (23) being dependent on a temperature sensor (22) in the vicinity of diffuser (6).
11. Apparatus according to claim 8, characterized in that the ceiling elements are provided with devices (13) for direct, heat-conducting fitting to the building-side ceiling (8).
12. Apparatus according to claim 8, characterized in that the ceiling members comprise metallic rectangular tubes arranged in lamellar manner, the rectangular tubes being provided with devices (13) for the edgewise fitting to the ceiling (8).
13. Apparatus according to claim 8, characterized in that ceiling members formed by tubular fins (5A, 5B) are provided and that in the downwardly directed wall area of the tubular fins openings (9) are provided, through which is brought about an intensified heat exchange between the fin wall and the room air, exclusively in the vicinity of the fins.
14. Apparatus according to claim 7, characterized in that diffuser (6) is provided with means for direct connection to the heat exchanger on one side of the room facing a window or front wall (7).
Priority Applications (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CH3933/86A CH672833A5 (en) | 1986-09-30 | 1986-09-30 | |
| PCT/CH1987/000129 WO1988002464A1 (en) | 1986-09-30 | 1987-09-30 | Process and installation for air conditioning of rooms |
| DE3750179T DE3750179D1 (en) | 1986-09-30 | 1987-09-30 | METHOD AND DEVICE FOR ROOM AIR-CONDITIONING. |
| JP62505587A JP2509652B2 (en) | 1986-09-30 | 1987-09-30 | Methods and equipment for air conditioning in rooms |
| EP87906063A EP0298996B1 (en) | 1986-09-30 | 1987-09-30 | Process and installation for air conditioning of rooms |
| CA000551165A CA1324021C (en) | 1986-09-30 | 1987-11-05 | Method and apparatus for the air conditioning of rooms |
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CH3933/86A CH672833A5 (en) | 1986-09-30 | 1986-09-30 | |
| CA000551165A CA1324021C (en) | 1986-09-30 | 1987-11-05 | Method and apparatus for the air conditioning of rooms |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1324021C true CA1324021C (en) | 1993-11-09 |
Family
ID=25671575
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000551165A Expired - Fee Related CA1324021C (en) | 1986-09-30 | 1987-11-05 | Method and apparatus for the air conditioning of rooms |
Country Status (6)
| Country | Link |
|---|---|
| EP (1) | EP0298996B1 (en) |
| JP (1) | JP2509652B2 (en) |
| CA (1) | CA1324021C (en) |
| CH (1) | CH672833A5 (en) |
| DE (1) | DE3750179D1 (en) |
| WO (1) | WO1988002464A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4015665C3 (en) * | 1990-05-16 | 1995-06-01 | Schmidt Reuter | Air conditioning system for multi-room buildings |
| DE4308969C1 (en) * | 1993-03-22 | 1994-07-28 | Schmidt Reuter | Cooling ceiling with inlet channel |
| DE4308968C1 (en) * | 1993-03-22 | 1994-07-14 | Schmidt Reuter | Cooling ceiling with air plenum chamber |
| CH711401B1 (en) | 2015-08-03 | 2019-05-15 | Erne Ag Holzbau | Concrete composite element for a ceiling element for room temperature control of a lounge. |
| GB2558625B (en) | 2017-01-11 | 2020-01-01 | Sporting Edge Uk Ltd | An air conditioning assembly |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE915386C (en) * | 1941-07-30 | 1954-07-22 | Maschf Augsburg Nuernberg Ag | Air flow in air conditioning systems, especially for large rooms |
| CH459512A (en) * | 1966-07-05 | 1968-07-15 | Sulzer Ag | Method and device for introducing supply air |
| FR2126601A5 (en) * | 1971-02-12 | 1972-10-06 | Govignon Fernand | |
| DE2222691A1 (en) * | 1972-05-09 | 1973-11-22 | Aschenbrenner Fa Franz | METHOD AND DEVICE FOR DEHUMIDIFYING ANIMAL TUBES |
| DE2462078A1 (en) * | 1974-05-17 | 1975-11-20 | Heinz Eichholz | Stale air shaft for stable air conditioner - providing minimum air flow rate to avoid smells |
| CH600254A5 (en) * | 1976-05-21 | 1978-06-15 | Kicon Ag | Multi-storey building air conditioning system |
| GB2029004A (en) * | 1978-08-19 | 1980-03-12 | Downing J | Ventilated roof |
| NL7902350A (en) * | 1979-03-26 | 1980-09-30 | Schellens Werktuigenbouw B V | VENTILATION DEVICE. |
| US4334577A (en) * | 1980-01-11 | 1982-06-15 | George Robert M | Ventilating system for livestock houses |
| GB2155170B (en) * | 1984-03-05 | 1987-06-03 | Waterloo Grille Company Limite | Adjustable ventilators |
-
1986
- 1986-09-30 CH CH3933/86A patent/CH672833A5/de not_active IP Right Cessation
-
1987
- 1987-09-30 DE DE3750179T patent/DE3750179D1/en not_active Expired - Fee Related
- 1987-09-30 JP JP62505587A patent/JP2509652B2/en not_active Expired - Lifetime
- 1987-09-30 EP EP87906063A patent/EP0298996B1/en not_active Expired - Lifetime
- 1987-09-30 WO PCT/CH1987/000129 patent/WO1988002464A1/en active IP Right Grant
- 1987-11-05 CA CA000551165A patent/CA1324021C/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPH01501335A (en) | 1989-05-11 |
| EP0298996A1 (en) | 1989-01-18 |
| EP0298996B1 (en) | 1994-07-06 |
| WO1988002464A1 (en) | 1988-04-07 |
| DE3750179D1 (en) | 1994-08-11 |
| JP2509652B2 (en) | 1996-06-26 |
| CH672833A5 (en) | 1989-12-29 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKLA | Lapsed |