EP1218673A1

EP1218673A1 - Method for regulating the climate in a room

Info

Publication number: EP1218673A1
Application number: EP00979403A
Authority: EP
Inventors: Joachim Paul
Original assignee: Integral Energietechnik GmbH
Current assignee: Integral Energietechnik GmbH
Priority date: 1999-10-08
Filing date: 2000-10-05
Publication date: 2002-07-03
Also published as: US6619053B1; DE19948654C1; CA2386812A1; ZA200109288B; AU1691801A; CN1125281C; JP2003511649A; KR20020027343A; WO2001027541A9; CN1353804A; WO2001027541A1

Abstract

The invention relates to a method for adjusting and maintaining a desired room climate with regard to temperature, humidity and carbon dioxide concentration at a given charge of heat, humidity and carbon dioxide. A fitting amount of outer air is cooled to a saturation temperature and is thus dehumidified. The saturation temperature results from the intersecting point of the saturation curve of humid air and a straight line which extends through the point of state of the air being in the state of the desired climate of the room air and the point of state of the available outer air in an h,x-diagram (Mollier diagram), i.e. is provided with a rise of the quotient of the heat charge in relation to the humidity charge (δh/δx).

Description

Procedure for climate control of a room

The invention relates to a method for climate control of a room.

It is desirable to set a comfortable indoor climate in rooms, i.e. to achieve environmental conditions at which the thermal, physical and hygienic parameters are within limit values, which lead to no (or only statistically minor) complaints and are even perceived as extremely pleasant. The desired comfortable room climate is usually created by air conditioning and ventilation systems.

Devices that condition the indoor climate in terms of temperature and humidity are commonly referred to as air conditioning systems. Another factor affecting the indoor climate is the dilution of pollutants, mainly the removal of anthropogenic CO ₂ , but also other pollutants, such as smells, air pollutants, etc. At the same time, water (steam) must be removed as a result of breathing, sweating, etc. Usually, heat must also be dissipated through the transmission of heat through human or mechanical heat sources in the room.

The removal of these heat, moisture and pollutant loads is compensated for by a conditioned supply air into the room in order to maintain the desired room air condition. In particular, the desired removal of pollutants requires the supply of clean air, which is usually taken from the outside as so-called outside air and the amount of which is determined by the increase in the indoor concentration depending on the concentration in the outside air.

So far, this outside air supply has been effected with air treatment systems (hereinafter referred to as air conditioning systems), which ensure a defined room air condition by supplying outside air, removing room air and by cooling and heating outside and / or room air.

From DE 36 10 069 AI a method for climate control of a room is known, which is based on the actual values of heat load, moisture load and carbon dioxide load and the desired target values of temperature, moisture and carbon dioxide concentration. is determined at which the outside air is cooled to a saturation temperature and thus dehumidified.

From Recknagel, Sprenger Schramek, Taschenbuch für Heizung und Klimatechnik, Oldenbourg, 1999, pp. 310 - 312, 326, 327, it is also known to regulate the indoor climate to the carbon concentration.

The object of the present invention is to provide a method for controlling the climate of a room with little expenditure on apparatus and little energy, which is improved in terms of its hygienic quality, in particular the carbon dioxide concentration) compared to previous air conditioning systems.

According to the invention, this object is achieved by the features of claim 1, the subclaims indicate advantageous developments of the invention.

The invention is based on the following consideration: by cooling only the supplied outside air, a desired (comfortable) value with regard to the temperature and air humidity can be obtained, to which supply air which is precisely defined in its state is supplied. The heat load can be specified as Δh in kJ per kg and the moisture load as Δx in grams of water per kilogram of dry air in the h, x diagram, these values can be represented as distances in the h, x diagram. The supply air condition must be selected in terms of temperature and humidity so that it can absorb the heat load Δh and the moisture load Δx. The mixing point of supply air and room air (mixed air) must therefore - based on the room air - be lower by Δh and Δx.

The condition of the supply air with regard to air humidity is determined so that it is saturated with water vapor. If you connect the state point of the room air and the mixed air to each other in the diagram, you get a mixture line whose intersection with the saturation line corresponds to the state of the humid air (supply air state). Since only intensive quantities are given in the h, x diagram, the supply air quantity (as mass or volume flow in kg or m ³ per unit of time must be calculated separately. This shows that the supply air quantity is greater than the current hygienic rules regarding the The air in the room is not only at the desired temperature and humidity level, but is also poorer in carbon dioxide and therefore more hygienic.

Such a method has not been used in the prior art, rather, in conventional air conditioning systems, recirculated air or mixed air (ie recirculated air and the required outside air) is dehumidified by cooling to such an extent that it can absorb the moisture load as supply air. However, the air temperature is so low that the air must be reheated. This reheating means additional equipment expenditure, which also entails unnecessary energy expenditure.

A cooling of only outside air to a low temperature according to the invention previously stood in the way of the prejudice that particularly expensive and special cooling processes are required for this, which increase the equipment and energy expenditure in such a way that the additional equipment and energy expenditure due to the reheating prove to be more favorable ,

According to the invention, however, the use of a pumpable liquid / ice mixture creates the possibility of reaching an arbitrary state point of the air in the h, x diagram, an additional advantage being a small heat exchanger area.

It is also advantageous that an outside air flow is divided into two air flows after passing a valve. Possibly. fans can be used to promote these air flows. Only a partial flow is cooled in a heat exchanger to such an extent that it can be mixed with the first partial flow in a mixing chamber, the temperature after passing through the heat exchanger and the partial flow ratio between the partial flows being selected so that the so-called fog region is reached in the mixing chamber becomes.

This will create a mist in the mixture, which will be used to separate the water into a drain pipe. Another discharge line is already provided in the cooling device.

The device dehumidifying the fog can e.g. work via capillary forces, as a wick or as a fiber mat or via so-called demister (regular or irregular) devices made of metal, plastic or fiber fabrics, which are also known as "so-called demister candles". In this way it can be achieved that only a small volume flow is to be passed over a heat exchanger and this can therefore be produced with a smaller heat exchange surface than would be the case if the entire air flow were passed through.

It is no longer necessary to heat up one of the partial streams after separating water, as has been customary up to now.

The further desired cooling will be achieved in terms of energy efficiency if a coolant made of pumpable, liquid ice pulp is used as the cooling supply for the air cooler, which is generated anyway at temperatures below the freezing point of water and provides a strong cooling of the air here, so that a larger air flow can be fed directly to the dehumidifier without cooling that can. Such an ice slurry can be stored and therefore requires a low installed capacity.

The supply air should not be introduced into the room in unmixed form, since the cold-dry air causes an uncomfortable feeling of a person in the room. In particular, it is proposed to allow the conditioned air to enter a nozzle through a control valve and to introduce it into the room as mixed air.

A conical sleeve, which can be moved along the extension of the nozzle, enables the so-called induction of room air. Another air jet outside along the sleeve will immediately mix with the induced air and form an air jet which is influenced in volume and temperature, but which essentially corresponds to room temperature.

Upstream of the nozzle is a valve, by adjusting and determining the displacement of the sleeve, the volume introduced and the type and amount of the induced room air can be determined, whereby a desired room air condition is set in a residence zone.

The insertion nozzles can preferably be attached to the ceiling, whereby a so-called air shower can also be provided in the room of the entrance doors, which means that people who enter the room with high temperatures can quickly get used to a cooler room climate, since they are already some distance away from the door is more mixed with the room air. At the same time, the known door effects, namely the penetration of warm air, can be avoided. If necessary, both the valve regulating the supply and the adjustable displacement of the cone can be influenced by means of a remote control.

In order to maintain the necessary dehumidification, it has previously been necessary to cool all the air supplied below the dew point, to allow water vapor to condense and then to warm the air again. However, this requires significantly more energy.

In an h, x diagram (Mollier diagram), the mixing line should run between the point of the desired room air condition (characterized by air pressure, room air temperature and humidity) and the point of the air condition of the outside air cooled to moisture saturation. A slope is realized that can be described by ι / _Δx , where q is the heat load in kJ / kg and Δx is the moisture load in grams of H ₂ O per kilogram of dry air. Further features and advantages result from the following description of a preferred exemplary embodiment with reference to the attached drawing. It shows:

1 shows the schematic structure of an air conditioning system according to the invention,

2 shows an h, x diagram for the air conditioning system according to FIG. 1,

3 shows a conventional air conditioning system,

4 shows an h, x diagram for conventional air conditioning systems according to FIG. 3,

5 shows a second embodiment of the invention,

6 shows an h, x diagram for cooling with an air conditioning system of the structure according to FIG. 5,

Fig. 7 is a schematic representation of the cooling process for the air, and

Fig. 8 is a schematic representation of the discharge nozzle for the air conditioned in this way.

An air flow of the outside air (ambient air), designated 7, for example, a temperature of 27 ° C. and 73% relative humidity is drawn in for a room. The volume flow will result at the end of the calculation. According to the invention, this air is cooled below the dew point via an air cooler which is operated with a liquid ice mixture, condensate forming, which is removed (FIG. 1).

The outside air flow and the amount of condensate discharged are chosen so that a desired comfortable air temperature and humidity of, for example, 23 ° C and 40% relative humidity is maintained in the room by the cooled and dehumidified air can exactly absorb the heat load Δh and the moisture load Δx. Part of the room air is discharged as exhaust air to the extent that outside air is supplied to the room.

The supplied outside air is cooled and thus dehumidified in a heat exchanger, i.e. to a saturation temperature, which results in the h, x diagram (at the intersection of the saturation curve of the moist air and the extension of a straight line through the state point of the desired room air, this straight line passing through must pass a point that results from the Room air condition point is reduced in Δh (thermal load) and this resulting condition point is reduced by Δx (moisture load).

Cooled and dehumidified outside air can be supplied to the room either directly or by mixing in recirculated air (air flow 4) indirectly as supply air, the supply to the room having to be carried out in such a way that there are no unwanted drafts caused by excessively high air speed and / or low air temperature ,

When the cooled and dehumidified air is fed directly into the room as supply air, the cooled and dehumidified air 5 is advantageously mixed with a recirculated partial room air stream, this mixed air entering the room as supply air. The circulating air volume flow is arbitrary.

With the direct supply of the cooled and dehumidified air, this must mix with the room air as supply air in the room, with the indirect supply of the cooled and dehumidified air, the mixing takes place outside the room in a mixing chamber, in which the partial streams 4 and 5 become conditioned supply air be mixed. In both cases, the determination of the supply air status in the h, x diagram is the same (FIG. 2). The slope and position of the mixture line is determined from a triangle 10, 12 and 14. Starting from a point 12, which represents the roughness condition to be maintained, the point 10 is determined from the thermal load h by reducing 12 by the amount Δh.

The point 14 is determined from the moisture load Δx by reducing 10 by the amount Δx. This results in point 14.

From the now known points 12 and 14, the mixing line can be drawn, which intersects the saturation line of the moist air in point 16. This point 16 is the required state point for the cooled and dehumidified air, which enters the room with direct supply as supply air 3 or 6 or enters the mixing chamber with indirect supply as 5 and is then supplied to the room as supply air , Point 16 thus specifies the (low) saturation temperature to which the outside air must be cooled in order to maintain the required indoor air conditions.

3, on the other hand, the usual method is described. The outside air flow designated 7, which is fixed for hygienic reasons (for example 300 m ³ / h for 10 people) is mixed as 5 with circulating air 4 and then dehumidified by cooling. The air with poorer water vapor content is suitable for maintaining the air humidity in the room, but due to the necessary cooling it is too cold and must therefore be reheated, otherwise a desired room temperature could not be maintained, ie the room would become increasingly colder. Fig. 4 shows the course of the changes in the state of the air flows in the h, x diagram, outside air from state 20 and recirculated air from state 30 (identical in temperature and humidity to the room air) and reach the mixing point 32. This mixed air must have a water vapor content brought, which corresponds to that of points 24 and 26 respectively. As with the embodiment according to the invention, the required state of the supply air flow - starting from room air 30 - is determined by correction by Δh (point 28) and Δx (point 26). This point 26 is accordingly achieved in that air is brought from state 32 to state 24 by cooling (-> 22) and water vapor condensation (-> 24). The air, which is now too cold, from state 24 must be brought to the state according to 26 by reheating.

A variant of the invention is shown in FIG. 5. The difference lies in the fact that the outside air flow is divided into two partial flows, a part (7) remaining untreated, a part (8) being cooled so far that the fog region is reached when these partial flows are mixed in a mixing chamber 9.

FIG. 6 shows how, when two air flows of states 34 (partial flow 7 of the outside air in FIG. 5) and 36 (partial flow 8 of the cooled outside air in FIG. 5) are mixed, a mixing point is reached on the mixing line, which - viewed geometrically - is below the saturation line. During the mixing process, water vapor also precipitates in liquid form (namely, as a "mist"), which can be removed from FIG. 5, which results in an end point 38 which arises from the mixing point. This point 38 is identical in terms of temperature and air humidity (saturated) to the air state 16 in FIG. 2. The advantage of this embodiment is that an even smaller air volume flow has to be cooled.

The invention according to FIGS. 1 and 2 or FIGS. 5 and 6 has the advantage that, based on the exemplary numbers and in comparison with the conventional method, only about a third of the air volume has to be cooled, approximately 2.5 -fold higher outside air rate is supplied, which considerably improves the hygienic conditions, while at the same time 20% less cooling power and no heating power are required and about 20% less electrical power is required

7, the space to be cooled is indicated by reference number 110. Air is drawn into this room via a device 140. Air supplied can be obtained from the environment 112 with the aid of a device 114, with only a small partial flow 118, which should be dimensioned in the case of insignificant cooling only in such a way that mist is formed in the device 124, is passed through a heat exchanger 122, which is advantageously cooled with ice pulp. This ice slurry is fed in and out through lines 142. Instead of, for example, 14.9 kW of power for cooling down to the dew point and a further 7.1 kW of warming-up power in total compared to an outside temperature of e.g. B. 27 ° C and an external humidity of 73% relative humidity (phi AL) indoor temperature of 23 ° C and 40% RH (and further indoor heat source of 5 kW and a moisture source of 1 kg / h) only 12, 2 kW power without warm-up power required.

To support the air flow in the individual sub-lines for the air flows 116 and 118, fans 120 can preferably be provided in each case. The formation of mist in the device 124 causes the moisture to be removed via a demister 126, which discharges the water directly from the process with discharge lines 128.

Finally, between the dehumidifying device 124 and the cooled room 110, the mixing device shown in FIG. 8 with the room air is to be provided, in which tapered at its end via a nozzle 130, as shown in FIG At the end, an inner wall 144 of a sheath 134 running parallel thereto is placed, which in turn, displaceable by a distance A along the nozzle, provides for different admixtures of a room air flow 134, 136. An actuating valve 138 for regulating the amount of air supplied is provided in front of the nozzle.

Subsequently, the partial flow 118 is cooled in a heat exchanger 122 to such an extent that it can be mixed with the first partial flow 116 in a mist generator 124, the temperature after passing through the heat exchanger 122 and the partial flow ratio between the partial flows, which are identified by reference symbols 116 and 118 are to be chosen so that the so-called fog region is reached in the fog generator 124.

This will create the mist, which with the device adiabatically dehumidifying the mist e.g. is dehumidified via capillary forces in the form of a wick or as a fiber mat or via so-called demister. In this way it can be achieved that only a small volume flow (namely 118) has to be passed over the heat exchanger 122 and it can therefore be produced with a smaller heat exchanger area than would be the case if the entire air flow were passed through.

Nevertheless, the entire air flow is drained in more than sufficient quantities. The simultaneous cooling can be done by supplying the air cooler with a pumpable, liquid ice pulp, which is generated at temperatures below the freezing point of water anyway and provides a strong cooling of the air, so that a larger air flow can be supplied directly to the dehumidification without cooling. In particular, it is advantageous that the outside air flow (provided with reference number 112) is divided into two air flows, the conduction paths of which are designated 116 and 118, after passing through a valve 114. Possibly. fans 120 can be used to promote these air flows.

For the introduction of the supply air into the room, it is proposed, in particular, to allow the conditioned air to enter a nozzle 130 through a control valve and to introduce it into the room as a supply air jet 132.

A conical sleeve 146a, 146b, which is displaceable by A in relation to the nozzle 130 along its extension, enables the so-called induction of ambient air, which is sucked in at the point designated by reference numeral 134. Another air jet 136 on the outside along the sleeve 134, like the air jet 134, will immediately mix with the induced air and will affect a volume and a volume and temperature, but will essentially form an air jet that corresponds to room temperature.

A valve 138 is connected upstream of the nozzle, by adjusting it and by determining the displacement of the sleeve 134, the volume introduced and the type and amount of the induced room air can be determined, as a result of which a desired room air condition occurs in a residence zone 110 (see FIG. 7) established.

The insertion nozzles can preferably be attached to the ceiling, and a so-called air shower can also be provided in the room of the entrance doors, as a result of which people who enter the room 110 with a high temperature are quickly accustomed to a cooler room climate, since they are some distance from the door is already more mixed with the room air. At the same time, the known door effects, namely the penetration of warm air, can be avoided. If necessary, both the valve 138 in the displacement of the cone 119 can be influenced by means of a remote control.

Claims

PATENT CLAIMS

1.Procedure for climate control of a room, whereby the actual values heat load, moisture load and carbon dioxide load are determined and regulated to the target values temperature, humidity and carbon dioxide concentration and outside air is supplied to the room to be air-conditioned via an air supply in two separate partial flows, whereby one of the partial streams is first only cooled to a saturation temperature and then mixed with the other partial stream to form a mist with adiabatic removal of the condensed water droplets of the mist and then fed to the room to be air-conditioned.

2. The method according to claim 1, characterized in that the condensed water is removed by a demister device based on capillary action.

3. The method according to any one of the preceding claims, characterized in that the cooling of the partial stream (18) is carried out by a heat exchanger (22) cooled with ice slurry.

4. The method according to any one of the preceding claims, characterized in that the introduction of the outside air is mixed with ambient air.