FI105851B - Procedure and apparatus for controlling the interior climate of a building - Google Patents

Description

105851

Method and arrangement for controlling the indoor climate of a building

The present invention relates to a method for controlling the indoor air mast of a building by means of air conditioning comprising at least some of the following process steps: - indoor air quality control, wherein pure filtered outdoor air is introduced inside the building; humidity control, whereby the supply air is humidified and / or dried, and control of the use of heat energy, whereby part of the heat content of the exhaust air is transferred to the supply air.

The invention further relates to an arrangement for controlling the indoor climate of a building.

Today, most of the indoor climate in a building is controlled by means of air-conditioning. central air handling units, which, depending on the use of the building and 20 quality levels, include all or at least some of the above functions and the equipment they require. The air from the central air conditioning unit is transferred to and from the premises by means of • air distribution and exhaust ducts.

• *. ·. The disadvantage of such known solutions, however, is that tl, j 25 all air handling units are only required for a part of the year. No heating unit is needed in summer, and no cooling unit in winter. In conventional air conditioning # · · '*' units, the humidifying unit is only required during frosty periods, when the water content of the outdoor air is exceptionally • · · - —.....

· ... · 30 low, post-heating units only when humidifying

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. * .., · or dehumidification is in operation, etc. However, the equipment is constantly in the air stream and causes pressure drop, * * · • even though it is not involved in air treatment. As a result, the fan units are unnecessarily expensive, the electric motors 35 and the electricity consumption unnecessarily high, the sound level of the unit is 105851 unnecessarily high, etc. for this particular air treatment.

Another drawback is that the size of the AHU units is inappropriate. If one looks at the minimum airflow to make the various air handling processes work, it is found that they are very different from one another. The first minimum limit is set by the quality of the indoor air, that is, the impurities created by people and activities in the space, which must be removed by removing 10 and supplying an equal amount of treated outdoor air. This airflow cannot be lowered under any circumstances while the building is in use. If the building has a separate heating system, this airflow is often a design airflow for winter time use. However, in the last few years, so-called "building blocks" have become more common, especially in 15 large buildings, such as commercial and public buildings, meeting and leisure facilities, etc. air heating system, which means that the building does not have a separate heating system, but the air conditioning system also provides heating for the building 20. This is due to the reduced heat demand of the buildings due to better insulation, multiple-wall windows, etc., and on the other hand due to the increase in the internal heat generation of the buildings. The internal heat generation is. ·,; has grown in offices, for example,

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! 25 because of it. Reduced thermal power can be supplied with air · .1 with the supply air without unduly increasing the airflow and / or supply air temperature. Excluding the separate heating system · · '·' * saves both investment and maintenance costs, reduces the risk of water damage, etc.

• · · 30 However, the specific heat of the air is low, so *) '*: In order to provide sufficient heating power, the supply air flow will in most cases need to be increased approximately * * * compared to what air quality control would require. Usually this happens in the so-called. as return air,!,; t! In other words, only the airflow required for air quality control, ie about 50% of the total airflow, is taken through and removed through the heat recovery unit 105851 3 tons. The increase required for air heating, ie about 50%, is controlled by dampers through a bypass duct to return air. The flow resistance of the heat recovery unit 5 then drops to about 25% of the design value and the temperature efficiency generally increases. However, the fan units operate at 100% airflow and the flow resistances of the air handling units correspond to 100% airflow. Also, the front surface of the heat recovery units cannot be reduced due to summer use, as will be explained later. This results in too low an air face velocity for the heat transfer and a lower temperature efficiency than optimal dimensioning could achieve. All air handling units must be dimensioned for 100% airflow. 15 In winter use, humidification may be required in normal conditions. If the humidification is not done according to the requirements of the production process but for the sake of comfort, it is usually sufficient that the relative humidity of the indoor air does not fall below 30%. This means that 0 to 3.5 g H 2 O / kg dry air should be added to the air, depending on the outdoor temperature and relative humidity. Usually. 'for dew point humidification, ie when humidifying the air near the dew point, ie 100% relative humidity, an airflow of 0 · 25% of the design airflow would be sufficient, as well as f · 25 as of course for post-heating, ie the humidifier «· ...____________________: that the post-heating unit is at least four times oversized. This leads in practice to major problems * 'in control, poor performance, etc.

As the outside air temperature rises, the building's heat ..

30 the need decreases. This can reduce the supply airflow and / or lower the supply air temperature. In recent years there have been electricity: ·. • · · · · · · · · · · · · · · · · · · · · · · · · · · In addition to reducing the airflow, the flow resistance of the AHUs is lowered in proportion to the second power of the airflow, so that the power consumption of the fan units is reduced as the airflow is reduced in proportion to the third power of the airflow. By reducing the power consumption, the speed control devices can be killed in a relatively short period of time.

Thus, nowadays, the air conditioning system is often adjusted to produce a decreasing heating power as the outdoor temperature rises, first by reducing the supply air flow by lowering the rotation speed of the fan units and by reducing the return air flow by closing the return air damper. When the return air damper is fully closed and the outdoor temperature continues to rise, the supply air temperature will be lowered by reducing the heat supply to the heating unit. It is completely closed when the heat recovery equipment and the heat generation inside the building 15 are able to cover the heat losses. In a modern office building, for example, this happens when the outside temperature is 5-10 ° C. As the outdoor temperature rises further, the recovery rate of the heat recovery unit will begin to decrease. There are several methods to do this. Part of the heat transfer fluid 20 may be, for example, be controlled by the heat recovery unit the air inlet side. When the temperature has increased. '*'; sufficiently, for example, in an office building to about 15 ° C, warm • V. the capture unit is fully closed. Outdoor temperature; as the building continues to rise, the building needs cooling. This can be achieved by introducing an evaporative cooling unit and / or by starting to supply cooling power to the cooling unit. When both operate at maximum temperature difference, the supply air flow and extract air flow are increased, thereby increasing the cooling capacity.

«·» 30 The exhaust air can be supplied either to the evaporative cooling unit or to • open the damper by opening the damper. Often there are:. however, it is advantageous to utilize the outdoor cooling effect of 4 m m so-called. free cooling by supplying only • outdoor air to the supply air. As the cooling demand increases, the airflow 35 is always increased to 100%, which is achieved in the office building, when the outdoor temperature is about 20 ° C. Only then does the cooling unit be supplied with cooling power. However, the 100% airflow needed for cooling is almost never the same as the airflow needed for heating. A common feature for many years has been the reduction in the heat demand of buildings and the need for cooling. In many buildings, the specific consumption of heat and cold is now almost equal. Because of the smaller difference in air temperature during cooling, the result is that the airflow required for cooling is greater than the airflow required for heating, in many cases up to 1.5 times.

Typically, the air flows for different air handling processes could be: air quality management 0.5 15 temperature management heating 1.0 cooling 1.5 humidity management humidification 0.25 20 drying 0.25 post-heating 0.25 energy management .. - heat recovery 0.5 I · '«· \; -evaporative cooling 1.5 «I I _; 1 · [25 Of course, the values may vary widely depending on the type of building, function, and requirements. In addition, it should be emphasized that the system described above is a fairly high-• • 1 ·· marsh system with particular attention to, for example, minimizing electricity consumption. Often, for example, the above described speed control is replaced by 2 speed motors.

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. ···. As shown above, except for fan blowers, - · · All AHUs are: - 1 · contracted for most or most of the year idle * 1 1 in 35 airflow, due to the pressure loss they cause · «• ·« · · • · • · · 6 105851, however, consume electricity. Another major disadvantage is the accumulation of impurities on the surfaces of the equipment even when not in use, which unnecessarily increases the cost of maintenance. Also, the equipment cannot be serviced and cleaned even when not in use as it is still in the air stream.

A very serious drawback is, of course, the fact that almost all AHUs have to be dimensioned for a 1.5-β airflow compared to 10 air treatment process would require. Apart from this, of course, resulting in high investment costs, 6x oversizing makes it very difficult to control the treatment process.

There have been many attempts to resolve the above drawbacks 15. For example, FI publication 92867 discloses a solution in which heating, cooling and heat recovery units are combined into a single heat transfer circuit that manages all of these processes. This will significantly reduce investment costs. The pressure loss of the Central 20 air conditioner and the resulting electricity consumption can also be reduced. The number of serviceable components is also significantly reduced. However, the solution, however, has some weaknesses. Perhaps the most serious of these is that the heat exchanger has to operate over a very wide range of 11 «25 airflows and temperatures, making it difficult to control the air handling · .1 ·: processes, especially in the extreme. The equipment is also very sensitive, even small design errors can easily lead to malfunction. All equipment is still in the air stream, so maintenance 30 and / or cleaning requires stopping the equipment etc.

. ···. To overcome control difficulties, for example, U.S. Patent No. 67,259 discloses a combination of a heat recovery unit and an evaporative humidifier unit in which a portion of the supply air flow is passed past the heat recovery unit and the humidifier unit. This gives the system adjustability and • · «• · · ·«

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105851 7 also reduced pressure drop. However, the equipment must be dimensioned for the nominal airflow.

Such improvement proposals for a single AHU have been reported in many other patents. They usually solve one sub-problem, but bring with them other problems or limitations.

For example, the high airflow required for cooling has been reduced by introducing a portion of the cooling power directly into the air-supplied spaces with various convector and cooling boiler solutions. The airflow can be reduced, but this will result in double systems, since in any case, the central unit must be provided with a dehumidification, i.e. 15 cooling, to prevent condensation of the room equipment. This also means that maintenance and cleaning costs will at least double. At least investment costs do not decrease significantly, but on the contrary increase. Recently, the quality and public health significance of the mold problem caused by water damage to buildings has been revealed. Spreading water piping to all areas of the building without the necessity of necessity therefore seems extremely dubious.

._. f Similarly, heating is generally done by radio • · '. . ' or other room equipment. In combination, • · «25 reduces the airflow of the central air conditioning unit • ·« '· * | to the minimum level required for air quality. It retains all previous functions of J * and provides two additional · »: * ·· systems, room-specific heating and cooling * · · ............

· System of cooling. The investment cost is not lower, at least, the cost of maintenance will increase significantly, plus; ***; all water solutions in the building must be fitted with two water · · ·. ···. the piping. Also, electricity consumption is not according to experience. * · 'There is no big difference, as the room appliances consume electricity.

The purpose of the invention is to provide a solution that can overcome the drawbacks of the prior art. 9 9 9 9 9 9 9 9 9 9 105 9 8 9. This has been achieved by the invention. The process according to the invention is characterized in that each process step is carried out in the said process. by means of one or more AHUs designed for the airflow required for the phase.

The arrangement according to the invention, in its turn, is characterized in that the means for carrying out each process step are formed in the said process. airflow unit dimensioned by the airflow required for the phase.

The advantage of the invention is above all that the electric power of the electrical 10 is reduced by up to half and the annual electricity consumption by less than half compared to the conventional solutions used previously. The investment cost of a central air-conditioning machine will be reduced by up to half the cost of the machines in existing systems. All AHUs except the fan-15 units can be serviced and cleaned while the central air conditioner is running. All air handling processes become easily adjustable. The sound level of the mainframe is significantly reduced compared to previously known solutions. Air handling units are in the air-20 flow only when the required air handling process is required. This significantly reduces fouling and reduces cleaning costs. When there are only \\ the Air Handling Units that are in the airflow. during use

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the pressure drop and thus the power output of the equipment is reduced

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! 25 consumption less than half. When each unit is sized for the minimum airflow of the process, the overall cost of the equipment is substantially reduced compared to prior art solutions. When the AHUs are in the air stream • · ·: Only when needed, of course, they can be serviced and cleaned at 30 other times, and they will not go out of operation -: *** of course. The dimensioning of the unit for the right airflow and operation with the required * * »airflow for the particular operating situation will significantly improve the controllability. As the pressure drop and airflow decrease, the sound level of the system 35 will also decrease.

• «· • · 105851 9

BRIEF DESCRIPTION OF THE DRAWINGS The invention will now be illustrated by the following detailed description of the accompanying drawings, in which Figure 1 is a schematic diagram illustrating a typical prior art arrangement for controlling the indoor climate of a building and Figures 2 to 9 illustrating various embodiments of the arrangement.

Figure 1 shows, in principle, a typical arrangement according to the prior art. For the sake of clarity, Figure 1 omits all parts irrelevant to understanding the solution, such as filters, shut-off valves, etc.

The arrangement of Figure 1 operates as follows.

Outdoor air, illustrated by an arrow A in Figure 1 through sucked the heat recovery unit 1, 1 ', 11 1 through the supply air side, where it is preheated by the exhaust air side 1' to the flowing heat. In Figure 1, the heat recovery unit is shown in a so-called. as a fluid circulation system in which heat is transferred from the outlet side 1 'to the heat transfer fluid, which is pumped through the conduit 11 to the supply air side 1 where it, ·. releases heat and returns through conduit 11

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back. There are many other heat recovery equipment available. In use, examples include a plate heat exchanger, * * j where heat is transferred directly through the metal plate from the exhaust air j * to the supply air, so-called. regenerative system with heat: 'bound to the mass of the rotating drum, etc.

From the heat recovery unit 1, 1 '11, air flows into the heating unit 3, where the air is heated by means of hot water, electricity, or the like, supplied through the pipeline 12. The next · · *** step is a humidifying unit 4, in which moisture is added to the air in the form of steam, by spraying with water or the like.

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way. This is followed by a cooling unit 5, in which the air • 35 is usually cooled by means of piping 13 • * «

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• · · · · 10 105851 with the help of water. The cooling unit can, of course, be formed by any other device, for example the evaporator part of the refrigerating unit.

When the air is evaporatively wetted, i.e. by misting it with water, it cools to near so-called. dew point, that is, a temperature where the relative humidity of the air is almost 100%. This temperature usually varies between 6 and 20 ° C, depending on the relative humidity of the outdoor air. If the cooling unit 5 is also used for dehumidification by cooling the air below the above dew point, a temperature too low for controlling the indoor air temperature, usually 8-14 ° C, will be required. Thus, in both cases, a post-heating unit 6 is required for air heating, which is supplied with heating power from the piping 14, from the electric grid 15, etc. The air is then distributed to the air-conditioned space 32 by the fan unit 2. The air distribution is illustrated by arrow B.

The air is removed conditioned is the state of poistopuhal-fan units 7. The exhaust air devices are described in the arrow C. Poistopuhallinyksiköltä 7 the air flow to the evaporative 20 cooling unit 8, which is used for cold recovery as described above and in the heat recovery unit, the exhaust air side 1 'to the outside, which is illustrated by arrow D.

• 1 • ·. ·. ·. For many reasons, such as heating a building ·. ; 25 at night, when little or no outdoor air is required, most of the exhaust air sucked by exhaust fan unit 7 is returned to the air-conditioned space by completely closing exhaust duct 10 and supply air damper 16, or * · · Partially and simultaneously open the recirculating air damper 9, respectively 30, whereby the exhaust air flows through the recirculating air duct 15 to the supply air equipment 2-6, where it is treated as desired and returned to the condition to be ventilated 32.

; ·] The order of AHUs in the hardware '... may vary. Likewise, a unit, such as a humidifier 4, may be missing or, for example, dehumidified • • t t I «i

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105851 11 may have its own separate unit, etc. However, the hardware shown includes all the most common devices in perhaps the most commonly implemented order.

The drawbacks of the arrangement of Fig. 1 are the very points which are disclosed in the prior art part of the description.

Figures 2 to 5 show exemplary embodiments of a complete apparatus comprising all AHU processes. However, in order to clarify the basic idea of the invention, a simple system according to Fig. 6, for example for an industrial hall, where only air quality control, temperature control by heating and energy use by heat recovery and evaporative cooling, is required. It is also assumed that the airflow required to control air quality is 7 m3 / s and the airflow required for heating is 14 m3 / s. According to the basic idea of the invention, each processing unit is sized according to the invention. the minimum airflow required for treatment. For purposes of comparison, the design values of the conventional system of Figure 1 are also summarized in the table below. The humidifier unit 4, the cooling unit 5 and the post-heating unit 6 would be omitted from the device of Figure 1.

«« • · t «· •» 1. ' \ 25 invention ordinary • «· '; heat recovery unit 1,1 '7 m3 / s 14 m3 / s • · · · · —j Γ tj' supply air blower 2 14 m3 / s 14 m3 / s • · _ ♦ 2 heating unit 3 7 m3 / s 14 m3 / s • · · V · 1 exhaust fan unit 7 7 m3 / s 14 m3 / s 30 evaporates. cooling unit 8 7 m3 / s 14 m3 / s 2 It is already apparent from the design values that the power consumption and investment cost of the system of the invention are considerably lower than normal. , • · 35 because the air flows are smaller.

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I »• · • · 2 • · 1 12 105851

The system of Figure 6 operates as follows. In the winter, in the heating design, the dampers 16 ', 10' and 20 are closed and the other dampers are open. The supply air fan sucks outdoor air A necessary amount of air quality control 5 7 m3 / s via a damper 16 of the heat recovery unit 1 through a supply air side, whereby the air is heated. In addition, it draws in recovery air C4 at 7 m3 / s through damper 17 through heating unit 3, whereby the return air is heated to a slightly higher temperature so that when the outdoor air flow and return air flow C4 converges in duct 15, the mixture temperature is suitable to cover building heat loss. The combined supply airflow of 14 m3 / s is blown into the room to be ventilated with the supply air blower 2.

In the system of Figure 1, the supply air flows through both the heat recovery unit 1 and the heating unit 3, but in the apparatus shown in Figure 6 according to the invention, part flows only through the heating unit 3 and some flows only through the heat recovery unit 1. Similarly, in the case of Figure 1, the exhaust air flows through both the evaporative cooling unit 8 20 and the heat recovery unit 1 ', in the apparatus of the invention only through the heat recovery unit 1f. It is clear, therefore, that the same design criteria for the airflow liV. in addition, the pressure drop in the apparatus according to the invention is <, v. smaller than conventional central air-conditioning machines.

»· · 25 The air flows listed above apply to the case where the heating medium of the heating unit 3 is a conventional 70 degree 1 hot water. Typical air temperatures after treatment * ·

• are then + 15 ° C for flow A, + 55 ° C for flow C4

V 2 and +35 ° C in the combined supply air flow.

30 Raising the temperature from about +22 ° C to +55 ° C in the heating unit 3 requires relatively more heating surface · 3: than raising the temperature from +15 ° C to +35 ° C in conventional / equipment. This situation is corrected by the realization of the principle of · · · FI 92867 that the circulating fluid of the heat recovery unit 1, 1 ”, 11 is supplied by i · '' J · '35.

Il f 2 i t 3

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105851 13 additional heat. It is particularly advantageous to do this, as shown in Fig. 7, by first supplying a 70 degree supply water to the heating unit 3, where the water cools to about 40 ° C, and the 40 degree water to the heat recovery unit 5, where it is further cooled. 25 ° C. The incoming heating water is marked with the letter F and the return water with the letter G. After treatment, the air temperature is 25 ° C in the outdoor air flow and 45 ° C in the return air flow C4. In addition to the reduction of the heating surface of the heating unit, a low heating water temperature is reached, which tends to remain at 25-40 ° C in air heating.

The advantage of the arrangement of Figure 7 is particularly apparent when considering what happens when the outdoor air temperature begins to rise, i.e. the heat requirement decreases. Tar-15 is irrigated in a situation where the heat requirement is reduced by 20%. Supply air flow B should also be reduced by 20% to keep electricity consumption to a minimum. As the outdoor air flow A cannot be reduced, the return air flow should be reduced, and in this case half of the 20 outdoor flows, it should be reduced by 40%. It will be immediately observed that the combined flow temperature of 35 ° C is not reached unless the return flow temperature in the case of Figure 6 is raised to about 68 ° C. Attaining such a temperature • · .y; 70 ° C water is virtually impossible. · .1 · 25, therefore, an acceptable drop in the combined flow temperature, for example, to 32 ° C, whereby the total airflow could be, 1 reduced by 12.5%. Worst of all, in the arrangement of Fig. 6, t · return air should be forced through the heating unit 3 V 'whenever a hot water is present. For example, when the heating need is reduced to half, ie, only the floating air flow A · · · ί ,,, ϊ would be sufficient to transport the required heat output, ie the return air flow C4 could in principle be shut down. **, the supply airflow B could be reduced by only 25% instead of 50% instead of 50%.

«* · T« · • · · · · i «1 2 I I f 14 105851

The problem can be solved by arranging the damper 28 and 26 and the bypass duct 27 for directing part of the outdoor air flow A to the heating unit 3 as shown in Fig. 8, of course, as well as the flow resistance of the apparatus 5. If the heating medium of the heating unit 3 is gas, electricity, steam, etc. instead of water, the problem is not as serious, but when the heat demand decreases to about 60% of the design value, it still exists.

Instead, in the solution of Fig. 7, the above problem is easily solved by increasing the heat output to the circulating fluid pipe of the heat recovery unit 1, 1 ', 11 so that the supply air temperature is 35 ° C. For example, when the heat requirement has been calculated, the 20% of the 15 design values after the outdoor air flow A temperature recovery unit 1 should be 29 ° C. When the need for heating power is reduced by half, the heat recovery unit 1 alone provides air heating.

As the outdoor temperature rises further, the current A of the outdoor air 20 is maintained but the heat supply to the heat recovery unit 1, 1 ', 11 is reduced, whereby the supply air B temperature decreases accordingly. When external heat is no longer needed, the heat supply is shut off. Until now, exhaust fan 7 has been operating at full power 25, and exhaust air has flowed out through damper 21, heat recovery unit 1 'and damper 10.

• m .1 As the outdoor temperature rises further and full heat recovery capacity is no longer required, the damper 10 'and • · ·' · 1 '16' will begin to open. The air currents 30 flowing through the recovery unit 1, 1 ', 11 are reduced, the air resistance of the apparatus is reduced, and ·· «· ... · The fan units 2, 7 can be adjusted to a lower rotation speed.

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* „, · To reduce power consumption. When the dampers 10 ',; ·, 16' are fully open, the dampers 10, 16 begin to close.

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As the outdoor temperature rises so high that heat recovery 35 is no longer needed, the dampers 10, 16 are closed and all • i · • · «» · ·

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• · 105851 15 Air handling units closed to the air flow.

As the outdoor temperature continues to rise, the cooling effect of the outdoor air can be exploited by increasing the outdoor airflow Ax by increasing the rotational speed of the fan 2, which requires that additional air be removed from the buildings. Another possibility is to run part of the exhaust air stream C, the evaporative cooling unit 8 and the heat recovery unit in the exhaust side 1 'through it, and part of the inlet air flow A 1 10 through the recovery unit inlet air side. It is also possible to make the recovery circuit 1, 1 ', 11' outside the cooling-transmission power, which the arrow F is shown in form. The choice depends on the heat load of the building, the ratio of outdoor and exhaust air temperatures, etc.

Figure 2 shows a complete system in which, in addition to the fan units 2, 7, the recovery unit 1, 1 ', 11, the heating unit 3 and the evaporative cooling unit 8, there is a cooling unit 5, a humidifying unit 4 and shut-off and / or damper 9, 9', 9 ' ', 18, 19. As can be seen in the figure 20, each' actuator unit can be disabled or partially actuated, if necessary, by means of dampers 9, 9 ', 10, 10', 16, 16 ', 17, 18, 19, 20 and 21. . . la. The airflow of each operating unit can be dimensioned and

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\! used to adjust independently of each other only to the extent I I t 25 as required by the particular air treatment process.

In Fig. 2, for each partial airflow Cx - C4, *: ** · has its own circulating air ducts 22 - 25. In most cases, the circulating air ducts are connected as shown in Fig. 3 and divided into: branches for different operating units 22 - 25 only 30 in the immediate vicinity of the mainframe. Of course, this can also be done partly, for example, by means of the branches 22 and • · ·. ···. 23, 24 and 25 are combined in pairs.

/ · * In the solutions of Figures 2 and 3, only the circulating air C from the room to be ventilated is taken from the processing units • ·: ** 3-6 32. Of course, the invention also includes the system according to Fig. 4. 16 105851 a solution in which dampers 29 and 30 and outdoor duct 28 allow one or all of the treatment units 3 to 6 to receive either outdoor air A2 or recirculated air C from room 32 to be ventilated, or both in the desired proportion.

Of course, such a possibility can also be provided for only a part of the processing units 3-6. If necessary, it may be provided that some or all of the treatment units take in only outdoor air A2. Of course, air intake through the damper 16 'is also possible.

Figures 2 to 4 show separate ducts for exhaust air C and recirculated air C. Especially when the duct network is large, it is usually advisable to combine the duct systems as shown in Figure 5 into a common duct system 31.

In Figures 2-5, the operating units are shown in principle connected in parallel. Partial or complete serial coupling is also within the scope of the invention. Fig. 9 shows a highly preferred embodiment in which the heating unit and the humidifying unit are connected in series. For clarity, the outlet side of the apparatus 20 and any other air treatment units are excluded.

In Figures 2-5, the humidifying unit 4 is in the exhaust air stream C2 alongside the heating unit 3. Suppose the hardware serves a state where you want to maintain at least \! At a relative humidity of 30%, i.e., at room temperature of 25 to 21 ° C, the water content of the air is 4,6 g H 2 O / kg k.i. Suppose '<«

* · 1j in addition to the supply air flow A to maintain air quality

: 'Is 7 m3 / s and the airflow for heating C4 is «·: 1 · 1 also 7 m3 / s. It is further assumed that the ambient air design temperature is -26 ° C with a water content of 0.4 g 30 H 2 O / kg k.i. Therefore, water vapor should be added to outdoor air flow A at 4.2 kg H2O / kg k.i.

• «·. ·· 1. The heating 3 as well as the humidifier 4

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The water content of the C4, C2 recirculated air is 4.6 g H2O / kg k.i., so there is no need to add moisture to them. In the humidifier unit «· 35 3 air can be evaporated as a dew point humidifier 105851 17 water about 3.5 g H 2 O / kg k.i. Evaporation binds the heat so that the air temperature drops to about 12 ° C.

In order to obtain a sufficient amount of water vapor, the 5 airflow through the humidifier unit 4 through the humidifier unit 4 should be (4.2 / 3.5) x 7 = 8.4 m3 / s, i.e. the design airflow of the fan unit 2 should be (7 + 7 + 8.4) = 22.4 m3 / s. In addition, to cover the heat consumption caused by wetting, the air stream C4 passing through the heating unit 3 should heat the wetting to a higher temperature corresponding to the heat consumption, i.e. after 55 the heating unit 3 should be 55.8 ° C instead of 45 ° C.

A much better result is achieved with the solution of Figure 9. Only the air flow C4, or 7 m3 / s, required for heating, is supplied through the heating unit 3, which is heated to 55.8 ° C. Thereafter, the dampers 17 and 19 control the partial air flow C4 through the humidifier unit. However, when the air temperature is 55.8 ° C, it is capable of absorbing significantly more moisture than air at room temperature, in this case 13 g H 2 O / kg k.i. At humidification, the air cools to about 21 ° C. The airflow C4 should be (4.2 / 13) x 7 = 2.25 m3 / s, i.e. only about a quarter of the airflow of Figures 2-5. The fan unit 2 is dimensioned. . The airflow is 14 m3 / s. To minimize power consumption, it is sometimes advantageous to equip the humidifier circuit with an auxiliary fan '· 1 ·' 25 33. If it has a speed control, damper 19 is not necessarily required to completely shut off the humidifier unit * · ''. If it is not desired to change the temperature after the heating unit 3, additional heat can be supplied to the recovery unit 1, · /: 1: 1 ', 11 as described above. The air current C2 then increases slightly.

. ···. The above embodiments are only examples of the possibilities of applying the basic idea of the invention. However, the examples are not intended to limit the invention in any way, but the invention can be modified freely within the scope of the claims. Therefore, the invention

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18 105851 covers, for example, all air treatment processes, although cooling and dehumidification are not shown in the examples. Of course, direct evaporative cooling is also within the scope, although only 5 indirect evaporative cooling are discussed in the examples. Likewise, all subsystems and components known per se are within the scope of protection, for example all known heat recovery methods, although the text and figures mainly refer to a fluidized system, which in some applications 10 offers considerable advantages. All known humidification methods, for example steam humidification, various forms of energy and production methods such as heat pumps, etc., are within the scope of the invention. It should further be noted that the invention also encompasses the use of a heat recovery unit for cold recovery in summer to cool the exhaust air so as to improve energy management. the evaporative exhaust air cooling unit and the cooled air are recovered cold in the heat recovery unit, where the direction of heat flow from the supply air to the exhaust air is changed. Further, the invention encompasses controlling the temperature of the indoor air when the air is dried by cooling the air below the dew point, which requires additional air heating in the post-heating unit to control humidity in the air. In each of the examples, there is one device for air treatment in Kuta. Within the scope of the invention! Of course, there is also an application where two or more devices connected in series or in parallel are available for some or '· * j for all functions due to high airflow, heating etc.'. • · · · For example, the supply air fan unit can consist of 30 two fans, one for circulation and one for outdoor air, allowing the supply air fan unit to be *** maintained and cleaned during operation. Of course, the invention also encompasses applications in which not all AHUs are adjacent to one another.For example, the exhaust fan unit and the exhaust air side of the heat recovery unit may be completely separate from the building. other units, wherein the input and out-toilmapuolen between the pipes is long. Similarly, for example, 5 supply air fan units can be located anywhere in the supply air duct system, etc.

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Claims (40)

1. A method for controlling the indoor air in a building by air conditioning, which method comprises at least some of the following process steps: 5. control of the quality of the indoor air, whereby clean filtered outdoor air is supplied to the interior of the building, - control of the indoor air temperature, whereby the supply air heating and / or cooling; - control of indoor air humidity, whereby the supply air is moistened and / or dried; and - control of the use of thermal energy, whereby part of the heat content of the fresh air is transferred to the supply air, characterized in that each process step is carried out with using one or more air treatment units (1, 1 ', 11, 2, 3, 4, 5, 6, 7, 8) that are dimensioned for the air flow required by the step in question. Process according to claim 1, characterized in that at least part of the air streams are changed according to the process step currently used. 3. A method according to claim 1 or 2, characterized in that at least part of the air streams are changed according to the load situation of the process step. • · • 'J. Method according to any of the preceding claims 1 - 3, characterized in that the power of the process step ·· is controlled by controlling the air flow. a · a * ... 5. Procedure according to some of the preceding claims. * Tent requirements 1 - 4, characterized in that through each treatment step it is controlled in different load situations. • 3. only the smallest possible air flow as load situation. ........ '... · tion in question requires. a 'j \ # 6. Method according to some of the preceding pairs, ···. Tent claims 1 to 5, characterized in that the process steps aa '·' which are not needed in the situation in question are excluded from the air stream. «A Process according to any of the preceding claims 1 to 6, characterized in that some or some of the process steps are carried out in the same air treatment unit. Method according to claim 7, characterized in that heat recovery from the fresh air and / or heating and / or cooling is made belt and poured or partially in the same air treatment unit (1, 1 ', 11). Method according to any of the preceding claims 1 - 8, characterized in that the heat recovery unit (1, 1 ', 11) is placed in a supply air stream which is to be conducted from the outdoor air into the building and in a extract air stream which is to be is discharged from the building, and the other air treatment units (2, 3, 4, 5, 6) are arranged in an etheric air stream which is taken from the building and led back to it. 15 Method according to any of the preceding claims 1 - 9, characterized in that the heat recovery unit (1, 1 ', 11) is placed in the supply air stream to be conducted from the outdoor air into the building and in the extract air stream to be discharged from the building. the building, and by means of the other air treatment units (2, 3, 4, 5, 6), the building is either supplied to the air taken from the outside air or to the eating air taken from the building or a mixed%; of these. A method according to any one of the preceding claims 1 - 10, characterized in that for each process step, the air handling units form a separate flow path from the outdoor air and / or the building. Method according to any of the preceding claims 1 - 11, characterized in that the flow paths from the building and / or the outdoor air to the air treatment units are combined completely and poured or partially. • · ... · 13. Procedure according to some of the preceding pa- · * · ,. Tent claims 1 - 12, characterized in that the heat and / or cooling power is measured in addition to the heating and / or cooling unit also to the heat recovery unit (1, 11). I i i r «<9 19 9 105851 Method according to any of the preceding claims 1 - 13, characterized in that the heating and / or cooling effect is measured alongside the heating and / or cooling unit for a further heating and / or cooling unit in the air flow. direction after the heat recovery unit (1, 1 ', 11) in the outdoor air stream. Method according to any of the preceding claims 1 - 14, characterized in that when the heating and / or cooling requirements of the building 10 are less than the dimensioned value, the heat and / or cooling power is measured only for the heat recovery unit (1, 1 '). 11) and / or to an additional heating and / or cooling unit in the direction of air flow after the heat recovery unit in the outdoor air stream. A method according to any of the preceding claims 1 - 15, characterized in that the substance carrying the heating and / or cooling effect is wholly or partly or firstly supplied to the heating and / or cooling unit and then to the heat recovery unit (1, 1). ', 11) and / or to another heating unit. in 17. A method according to any of the preceding claims 1 - 16, characterized in that the outdoor air flow «i i # '. But is wholly or partially controlled to the heating or cooling unit after the heat recovery unit (1, 1 ', 1 1). • Method according to any of the preceding claims 1 - 17, characterized in that a humidifying unit is arranged in the air stream # ... § 30 after the heating unit. * · I ” 19. A method according to any of the preceding claims 1 to 18, characterized in that only a part J of the air stream after the heating unit is controlled to the humidifier. 35 20. A method according to any of the preceding claims 1 to 19, characterized in that an auxiliary fan unit (33) is arranged in any air or in the air stream of some air treatment units (33). 21. Arrangements for controlling the indoor air in a building by air conditioning, which arrangement comprises at least some of the following means for carrying out process steps: - means for controlling the quality of the indoor air, which are arranged to supply clean filtered outdoor air to the building; 10. means for controlling the temperature of the indoor air, which are arranged to heat and / or cool the supply air, - means for controlling the humidity of the indoor air, which are arranged to humidify and / or dry the supply air, and 15. means for controlling the use of heating units. - gi, which are arranged to transfer part of the heat content of the fresh air to the supply air, characterized in that the means for carrying out each process step are formed by an air treatment unit (1, 20 1 ', 11, 2, 3, 4, 5, 6, 7 , 8) dimensioned using the airflow required by the step in question. Arrangement according to claim 21, characterized; , characterized in that at least part of the air streams are c a Y. · arranged to be changed according to the process step currently used. • · »···; An arrangement according to claim 21 or 22, i *. characterized in that at least part of the air streams are arranged to be controlled according to the loading stage of the process step. ... 30 Arrangement according to any of the preceding claims tent claims 21 - 23, characterized in that the power of the process step is arranged to be controlled by controlling the air. current. 25. An arrangement according to any one of the preceding claims 35 to claims 21 - 24, characterized in that through each (f · Y; and one treatment step is only the smallest possible air * (I in 105851 Current that the load situation in question requires is arranged to be controlled in different load situations. Arrangement according to any of the preceding patent claims 21 - 25, characterized in that the process steps 5 which are not needed in the situation in question are arranged to be excluded from the air stream. Arrangement according to any of the preceding claims 21 - 26, characterized in that some or some of the process steps are arranged to be carried out in the same air treatment unit (1, 1 ', 11). 28. Arrangement according to claim 27, characterized in that heat recovery from the fresh air and / or heating and / or cooling is wholly or partly arranged to be carried out in the same air treatment unit (1, 1 ', 11). Arrangement according to any of the preceding claims 21 - 28, characterized in that the heat recovery unit (1, 1 ', 11) is arranged to be placed in a supply air stream to be conducted from the outdoor air into the building and in a fresh air stream to be discharged from the building, and the other air treatment units (2, 3, 4, 5, 6) are arranged to be placed in an ether air stream taken | from the building and is led back to this one. · l Arrangement according to any one of the preceding claims 21 - 29, characterized in that the heat recovery unit (1, 1 ', 11) is arranged to be placed in the tile · · · • · ·· the air stream to be conducted from the outdoor air into the building and into the open air stream to be discharged from the building, and that through the other air treatment units (2, 30 3, 4, 5, 6), either supply air is taken from the outdoor air. · · · ··· Smile ether air taken from the building or a mixture of * · * these arranged to be led into the building. : "31. Arrangements according to any of the preceding claims 11 to 21, 30, characterized in that for the air conditioning units, the handling units in all process steps are a separate flow path formed from the outdoor air and / or the building. • · • · 105851 Arrangement according to any of the preceding claims 21 - 31, characterized in that the flow paths from the building and / or the outside air to the air treatment units are fully poured or partially combined. Arrangement according to any of the preceding claims 21 - 32, characterized in that the heating and / or cooling effect is arranged to be measured in addition to the heating and / or cooling unit also to the heat recovery unit (1, 1 ', 11 ). 34. Arrangement according to any of the preceding claims 21 - 33, characterized in that the heating and / or cooling effect is arranged to be measured alongside the heating and / or cooling unit for an additional heating and / or cooling unit in the direction of flow of air. after the heat recovery unit (1, 1 ', 11. in the outdoor air stream. 35. Arrangement according to any of the preceding claims 21 - 34, characterized in that when the building's heating and / or cooling requirements are less than the dimensioned value, the heating and / or cooling effect is arranged to be measured only at the heat recovery unit i «) (1, 1 ', 11) and / or to a further heating« ««; \ and / or cooling unit in the direction of air flow • <f '·' I 25 after the heat recovery unit in the outdoor air stream. t An arrangement according to any of the preceding claims, claims 31 - 35, characterized in that the substance which transports the heating and / or cooling effect is arranged to be wholly or partially guided first to 30. the heating and / or cooling unit and, therefore, ···. ···. is added to the heat recovery unit (1, 1 ', 11) and / or to another heating unit. »» • ”37. Arrangement according to any of the preceding patent claims 21 - 36, characterized by that. The outdoor air stream is arranged to be wholly or partially controlled to the heating or cooling unit 105851 after the heat recovery unit (1, 1 ', 11). 38. Arrangement according to any of the preceding claims 21 - 37, characterized in that a humidifying unit is arranged in the air stream after the heating unit. 39. Arrangement according to any of the preceding patent claims 21 - 38, characterized in that only part of the air flow after the heating unit is arranged to be directed to the humidifier unit. Arrangement according to any of the preceding claims 21 - 39, characterized in that an auxiliary fan unit (33) is arranged in the air stream of some or some air treatment units. ti (I «rf * t ι f · IIII tl (I • • · • · • · * · • 9 9 9 9 9 9 9 9 9 9 9 9 • 1 I »I« f «<·« t I f «· t« · II («IIII