Air conditioning device and method of room air conditioning

The invention relates to an air conditioning apparatus, which by the temperature in at least one chamber Ventilation with heated or cooled air to a predetermined temperature setpoint controls with the specified preamble of claim 1 features. The invention also relates to a method for Conditioning of a space of claim 8.

Cooling devices are in the air-conditioned Rooms in all seasons comfortable stay conditions creating, by the temperature and keep moisture of the room air within fixed limits and sufficient ventilation with fresh Air care.

In winter, the supply air temperature is higher than the ambient air temperature, when the air heat the room at the same time intended, and in the summer is the supply air with blowing a lower temperature, to the space on the to maintain desired temperature chamber air temperature.

Conventional air-conditioning units to circulate a typically excessive amount of air at the temperature of which is adapted to the heating and cooling requirements. there it is considered a disadvantage that even a Circulation of a large volume of air takes place when the desired set temperature is reached. In addition, there is a danger that the supply air through the supply air duct blown into the space and immediately above the exhaust duct to the space to be conditioned again leaves. There is a slight mixing of the new Supply air instead of the existing room air.

Furthermore, in the air conditioning of several rooms the problem is that different in the rooms Actual temperatures are present. An adaptation of the Temperatures on the comfort in any room Consideration for, is hardly possible.

From DE 40 04 519, the features of the preamble of claim 1 or disclosed by claim 8, is a supply and exhaust air unit combination Known for ventilation and / or air conditioning. Here, the exhaust air is used to cool the cooling unit used. The reference variable of the control therefore the exhaust air to a certain minimum exhaust air volume flow for cooling and thus the heat dissipation the cooling units to ensure.

From DE 42 21 177 A1 is an air conditioning apparatus known, which in an at least a space forming zone with a supply air supply air over an inlet air supplies and with an exhaust motor Exhaust air through the exhaust duct sucks. The space is divided into several Room zones divided. Between these spatial zones Different pressure gradients exist. With a Druckgradientenkontrollsystem is prevented be it to gas flows between neighboring Space areas comes. About the Druckgradientkontrollsystem the supply and the exhaust air motor is then controlled. For example, the performance of the air motor is increased, when the control system has a certain pressure gradient registered. The purpose of this device is a directed possible flow of air inlet nozzle for Abluftdüse. to deviate from these cross currents be avoided by regulation.

The present invention is based on the object, provide an air conditioning apparatus, the economic works behaglichere room conditions and an optimal mixing of the room air with the supply air ensured in order to adapt quickly to the heating, To achieve cooling, humidification and dehumidification setpoints.

This object is achieved by the characterizing features of claim 1 and of claim 8 combined with their respective Preamble thereof dissolved.

form Further advantageous embodiments of the invention the objects of the dependent claims.

The invention is based on the recognition that each greater than the pressure in a space to be conditioned is, the better the flow is through the space with the blown air supply. This warms the Room more quickly, the efficiency of the system is increased and large temperature fluctuations in the room, for example, above very warm and down very cool, but also temperature differences over the length and width of the room can be avoided.

A good flow of space ensures that heated in the shortest time with less amount of air a room, cooled, humidified or dehumidified. The lower air rate blown in is more pleasant perceived. For faster adjustment of the heating, Cooling, humidification and dehumidification setpoints is the efficiency of the air conditioning apparatus improved.

In particular, the target value for the Regulators Exhaust air motor, depending on the outside temperature and / or for the supply and / or the supply pressure certainly. This control of the exhaust air motor function on the outside temperature and / or for the supply and / or the supply air pressure for the optimization the flow through important. Namely, the higher the Supply air temperature or the supply pressure, the greater takes the pressure for a favorable flow be through the space to be conditioned with the incoming air. The deeper, however, the outdoor temperature, the higher is usually the supply air temperature and the higher must thus the overpressure in the room to be conditioned be. So there must be a greater pressure to ensure an optimal flow through the Room with the blown air supply exist.

Preferably, on the one hand, the actual value for the controller of the air motor through the channel differential pressure formed of which the difference between absolute value of the pressure in the supply air and the absolute resulting value of the pressure in the exhaust duct. In order to it is achieved that, for example in air-conditioning units for several rooms disorders of the overpressure by opening windows in each room and thus a resultant by regulating the exhaust air motor unintentional increase the overpressure in the other rooms due to pressure loss in the one Space is avoided.

On the other hand preferably results in the actual value for the controller of the motor exhaust air from the difference between the external pressure and the chamber pressure.

Here, especially the room pressure changes only over a predetermined temperature range of the outside temperature and / or for the supply with change the outside temperature and the supply air temperature, wherein at an ambient temperature before this temperature range the room pressure in each case a certain constant Size and at an ambient temperature or supply air temperature after this temperature range the room overpressure each having a more certain constant size. Particularly falls in the temperature range of Chamber pressure with the outside temperature rises from a maximum overpressure to a minimum pressure.

Two contradictory requirements is characterized bill carried. On the one hand it is a good Flow through the room to be conditioned needed that the pressure is as large as possible. On the other side must the pressure but not too big be because he is otherwise found to be unpleasant and when excessively high pressure to open doors themselves or not open or only with considerable force Open or suggest.

So that there is a comfortable and a Control Pressure regardless of the amount or the floor of ensuring room to be conditioned, is the room differential pressure at a level above 0 (room height) measured. Room height corresponds External height with respect to the sea level.

According to one embodiment of the invention the temperature the supply air and the channel pressure of the supply air with each other coupled such that both in response of the height of the room temperature to the amount of inlet air temperature as well as in function of the level the room temperature to the amount of the nominal value of the room temperature the channel pressure of the supply air into the room, the spaces is increased or decreased or room zones.

The advantage hereby achieved consist in particular that it is not a large volume tempered air is circulated unnecessarily, but only the volume, the maximum for a quick adaptation of the actual space values is required at the setpoints.

In this way, not only energy savings achieved, moreover, it is located on the in room People felt far more comfortable that a stronger air movement only takes place when the Temperature of the air blown far from the actual temperature differs. In conventional air-conditioning units on the other hand, especially during the morning warm-up even at room temperature, the strong is below the setpoint, only slightly warmed Supply air is blown into the rooms with high channel pressure. This has been by the persons concerned unpleasant, but regarded as inevitable.

According to this embodiment of the invention is therefore only heated air with a larger channel pressure blown into the room when the temperature of the supply air well above the predetermined desired temperature of the room and thus in particular in the warm-up far is higher than the actual value of the room. By a ratio control, wherein the channel pressure of the supply air in a set fixed relation to the supply air temperature is, can be a corresponding coupling of the channel pressure the supply air to the supply air temperature according to the invention realize particularly advantageous.

Preferably, the channel pressure of the supply air in the will Space, the rooms or room zones over the management of the supply air set.

can via a selector between two delivery behavior to get voted.

Firstly, for the heating mode, when the target value of Room temperature is less than the actual value of the room temperature , the channel pressure of the supply air with the room temperature rising reduced. Accordingly, for the cooling mode, when the target value of the room temperature is greater than the actual value of the room temperature, the channel pressure of Supply decreases with decreasing ambient temperature. On the other hand is for the heating mode, if the nominal value or the Actual value of the room temperature is less than the supply air temperature and the actual value of the room temperature is less than the setpoint of the room temperature are, the duct pressure the supply air increases with increasing air inlet temperature. correspondingly is for the cooling mode, if the nominal value or Actual value of the room temperature is greater than the supply air temperature and the actual value of the room temperature is greater than the Setpoint of room temperature are, the duct pressure with declining supply air temperature increases. The increase in the pressure channel the air is perceived as pleasant. moreover is the efficiency of the heating and cooling device improved, as shown below still running becomes.

According to a further embodiment of the invention changes the channel pressure of the supply air only over a predetermined temperature range of the supply air temperature. Assigns the supply air temperature at an altitude before this Temperature range, then the pressure of the supply air channel each associated with a certain constant size. Assigns the supply air temperature a height on the temperature range on, the channel pressure of the supply air is respectively assigned to another given constant size.

In particular, increases in a relation to the room temperature larger supply air temperature above the predetermined Temperature range of the channel pressure of the supply air from his Minimum performance to its maximum performance with increasing Supply air and falls accordingly with declining Supply air temperature.

The two schemes of Zuluftkanaldruckverhaltens is made possible on the one hand, that the efficiency of improves the air conditioning device becomes. With higher channel pressure of the supply air is also a faster and better flow through the space, and thus a rapid heating of rooms reached. On the other side is but reasons of comfort too large an air flow to be avoided, since this is perceived as unpleasant. This opposite Requirements is done now perfectly sufficient.

The control loop which regulates the pressure of the supply air duct, here is underlain the temperature control circuit, wherein the Zuluftkanaldruck setpoint at a fixed ratio is adjustable to supply air temperature actual value. This is too large overshoot and undershoot avoided in the temperature control. The Room temperature settles quickly to the setpoint temperature on.

In an air-conditioning of several rooms, the heated Supply all rooms on a common supply air duct made available. At different but desired and actual temperatures of all the rooms, each Space heating demand another. To this into account to wear, are in accordance with another embodiment, the invention in the air conditioning of the same multiple rooms or room zones, the individual rooms or Room zones via one assigned to them Zuluftund Exhaust air duct to the central supply and extract ducts connected and there are in the individual supply air and / or ducting arranged throttle, over which the pressure channel of the supply air in the space, the rooms or room zones is set.

This unwanted air movements in rooms can be avoided, their value and setpoint equal or approximately are equal. In addition, it is achieved that, for example, unnecessarily when fully open fresh air damper much fresh air is conditioned.

The control of the throttle valve can also function of supply pressure or the speed of the supply air done.

In such an independent regulation of supply air and individualer room temperature, a Situation may occur in which a single space as possible must be heated quickly, other rooms but which are already on target temperature possible little to be heated. The individual control this warm spaces is at the increased supply air try to close the throttle. In order to But are these spaces and located therein Persons cut off from the supply of fresh air.

This problem is according to another embodiment advantageously achieved that, even with a Inlet air temperature, which is above the target temperature, in rooms where the actual temperature to the desired temperature corresponds, the minimum required volume of fresh air is blown. In this way it is achieved that these Rooms are supplied with sufficient fresh air, nevertheless a possible warming of the premises as a result of Supply air temperature which is above the target temperature is, as far as possible avoided. The for specified minimum fresh air volume required minimum Throttle position depends on the supply air temperature and the proportion of fresh air from the air supply, because the proportion of fresh air to the incoming air is, if possible - Warming up in the morning - for a maximum fast reduced heating and replaced by convection.

According to one embodiment of the exhaust air duct and the supply air through a recirculation duct connected, wherein at least one exhaust air dampers in at the exhaust duct adjacent air duct, at least a mixed air damper in the return air duct and at least one in the upstream fresh air damper the air supply Fresh air duct provided.

According to a further embodiment, the minimum cross-section of the throttle valve in dependence on the Opening of the fresh air flap, the exhaust damper and the mixed air damper is set so that in each control situation ensures the minimum amount of fresh air becomes.

In controlled channel pressure of the supply air and exhaust air the opening positions of the mutually associated Throttle in a room or in a room zone equal.

Similar to the heating control can also be a cooling control done.

For the temperature control knob can be used. In practice these tend controller to overshoot and undershoot of the controlled variable.

According to a further embodiment of the invention respectively the manipulated variable at least one controller, in particular the temperature controller, to a downstream connected switching means and the switching means selects at an overshoot of the controlled variable a their predetermined value for the manipulated variable, the clear under the same selected from the regulator Value.

Such behavior can be beneficial by additional controller and a minimum selector realize. This additional controller provides a function of the control difference a predetermined minimum value for the manipulated variable, when an overshoot of the controlled variable occurs, and a predetermined maximum value for the manipulated variable, if the actual value of the temperature (the controlled variable) under the setpoint is. selects the minimum selector then from the from the regulator and of the additional control means provided values ​​respectively the minimum, and outputs the selected value as Manipulated variable on. In this way, assumes the additional Controller always control via the command value if the result of the manipulated variable Regulator overshoot occurs in the controlled variable.

are in accordance with another embodiment of the invention upstream a fresh air flap in the air supply channel Fresh air channel, a mixed air damper in a connecting the supply air with the exhaust air duct Recirculated air duct and an exhaust air flap in one at the exhaust duct adjacent air duct provided wherein the positions of the fresh air flap, the Exhaust air damper and the mixed air damper jointly as the speed of the supply air or the Channel pressure of the supply air to be regulated, and which up to a certain minimum aperture to ensure a Fresh air minimum with increasing speed of the supply air and / or with increasing pressure of the supply air channel the opening cross-sections of the fresh-air flap and the reduced exhaust damper and the opening cross-section the mixed air damper can be enlarged.

The opening position of the fresh air damper and the opening position exhaust air dampers are immer.gleich big. The opening position of the mixed air damper is always the difference in the opening position of the fresh air or Exhaust air damper 100%, z. B. the opening positions the fresh air damper and exhaust air dampers respectively 70%, then the opening position of the mixing air flap 30%. Tells the mixed air flap, an opening position from 70% to, as are the opening positions the fresh air and exhaust air dampers respectively 30%.

In a further preferred embodiment of the invention is more than an area of ​​a central facility air conditioned. Even with different heating requirements the individual rooms must have the air supply sufficient Heating capacity for all rooms available be provided. This can be achieved by, among other things, that the need for heating at the actual temperature of the coldest area is calculated to also use this space in short to bring time to target temperature. Therefore, according to an embodiment of the invention in air-conditioning of several rooms at the same time the actual temperature each room of a central control device supplied, and a single one of these actual values individually to be determined as a temperature value Value supplied for the heating controller.

According to a further embodiment of the invention is a humidifier provided the supply air the moistened in the supply duct, said humidifying both depending on the ambient humidity or the air humidity and the supply air temperature is regulated.

are in accordance with another embodiment of the invention a introduced into the supply air duct first heating device, one of the first heating device in the supply air downstream cooling device and one of the Cooler downstream in the supply duct second Heating device for heating, cooling and dehumidification of the supply air is provided, wherein the second heating device in dependence on the actual value of humidity is controlled to setpoint humidity.

In particular, increases with increasing actual value humidity, is already above the setpoint humidity, the heating power the second heating device.

The heat output of the second heating device either a regulator or regulated increases with increasing actual value over a predetermined humidity Humidity range of room humidity, at a room humidity before this moisture range the heating power has each a certain constant and at a Room humidity after the moisture range, the heating capacity each another certain constant size on.

This ensures that a dehumidification over Increase in the room temperature is effected, provided that the Actual value of the room temperature below the limit remains, from which the cooling operation is initiated. It is therefore only then cooled when the actual value of the room temperature greater than the target value of the room temperature plus dependent on the outside temperature, temperature shift is. By heating and thereby the dehumidification the space above the rising temperature the room quickly and with a comparatively low Energy expenditure dehumidified.

The channel pressure of the supply air during the dehumidification process not increased.

A minimum quantity of fresh air in the chamber or the Rooms to guarantee the control of Frischund done the air damper function of the opening position the mixed air damper.

In the simplest case, with the air conditioning device tempered one room and vented. The Control of a multi-room air conditioning is in the embodiment described in more detail with reference to the drawing. Show it:<dl tsize="7"><dt>Fig. 1</dt><dd>a schematic representation of the air circuit an air conditioning apparatus according to the invention;</dd><dt>FIG. 2</dt><dd>a block diagram with the most important Elements of the regulation and control devices the embodiment;</dd><dt>Fig. 3</dt><dd>a block diagram of the major elements the temperature control loop of FIG. 2;</dd><dt>Fig. 4</dt><dd>a block diagram of the flow volume loop of the supply air from Fig. 2;</dd><dt>Fig. 5</dt><dd>a block diagram of the individual Temperature control loop for each room from Fig. 2;</dd><dt>Fig. 6a</dt><dd>the relationship between the supply air temperature and the supply pressure for the embodiment, if the actual room temperature is less than the set point room temperature;</dd><dt>Fig. 6b</dt><dd>the relationship between the room temperature and the supply pressure for the embodiment, if the actual room temperature is higher or equal to the setpoint room temperature; </dd><dt>Fig. 7</dt><dd>the block diagram of the temperature controller of the Embodiment;</dd><dt>Fig. 8a</dt><dd>the block diagram of the controller of the air motor the embodiment;</dd><dt>Fig. 8b</dt><dd>the block diagram with the main elements of FIG. 8a;</dd><dt>Fig. 8c</dt><dd>the relationship between the outside temperature and the target value of the room differential pressure for the controller of the air motor;</dd><dt>Fig. 9</dt><dd>the relationship between the exhaust air humidity and the manipulated variable for the reheaters and</dd><dt>Fig. 10</dt><dd>a flow chart with the main on Heating process involved block diagram elements.</dd></dl>

In Fig. 1 is a schematic of the air circuit of a multi-room air conditioning shown. From the air conditioned Rooms 1 lead on the one hand supply air 5 to a supply air duct 10 and on the other Side exhaust pipes 6 to an exhaust air duct 11th

In the air supply line 5 is in each case a throttle 60 and in the exhaust line 6 each have a throttle 61 arranged.

The air supply conduit 10 and the exhaust duct 11 are a Recirculated air duct 12 connected to each other.

The supply air duct 10 is a fresh air duct 20 upstream and the exhaust duct 11 is an air duct 21 downstream.

In fresh-air duct 20 are a fresh air flap 70 in Recirculated air duct 12 a mixed air damper 72 and the exhaust air duct 21 an exhaust damper 71 is provided.

In the supply air duct 10 are in the direction of airflow succession a first heating device 30, a Cooling device 40, a second heating device 33, a supply motor 15 and a humidifying device 50 arranged.

In the supply air duct 10 is a through the supply air motor 15 Air pressure P_TO generated, which ensures that the supply air to be conditioned with sufficient flow volume in the Rooms 1 is blown.

Accordingly, in the exhaust duct 11 through the air motor 16 an underpressure P_FROM generated, the ambient air, the sucks.

In the simplest case, the pure ventilation case - office operation - Which sucked room air (= exhaust air) via air channel 11 and the exhaust air duct 21 to the issued outside air via the fresh air duct 20 is the required supply air and fresh air in the supply air duct 10 sucked. For this, the fresh air flap 70 and the exhaust damper 71 is opened and the mixed air flap 72 closed. The fresh air damper 70 and the Exhaust air damper 71 have always same opening positions on.

In order to allow heating of the air-conditioned rooms 1, flows through the fresh air sucked through the first Heating device 30 - preheater - over which the intake air depending on the heating requirement to the required supply air temperature T_TO is brought. After passing the non-energized cooling device 40 and the second heater 33 - re-heater - is they fed to the moistening device 50, which air supplies the necessary moisture.

Instead of the first heating device 30 is at a necessary cooling of the air conditioned rooms which Cooler 40 in operation. Too large humidity is, instead of humidifying 50, reheaters 33 for dehumidifying in operation. To a more rapid Heating to ensure both the first Heater 30 and second heater 33 to be in operation. However, this is for the heating mode, not for the Entfeuchtungsfall possible.

The so treated air is over the supply air motor 15, the supply air duct 10 and the air supply ducts 5 with Throttle 60 to be conditioned to the individual Premises supplied. The volume of each individual in single room blown and sucked air can through the supply air lines 5 and in the exhaust air ducts 6 arranged throttle 60, 61 individually be regulated.

With increased demand for heating, for example in the morning Warm-up phase, it is advantageous to the spaces not only to provide them with aspirated fresh air, but a portion of the extracted air repeatedly use, for and in the simultaneous warming Ventilation is the required supply air far over the fresh air minimum volume. Therefore, depending of the supply air temperature T_TO via a control device 500 in FIG. 2 is a control output y_V calculated and the air damper 550, in FIG. 2 or 70, 71 72 fed in FIG. 1.

While the fresh air damper 70 and the exhaust damper 71 receive the same control signal, the mixing air flap is 72 in the return air duct 12, the exact opposite Control signals are sent. The opening position the mixed air damper 72 is always the difference to the open position the fresh air flap 70 or the exhaust air dampers 71 to 100%. For example, the open position the fresh air damper 70 and the exhaust damper 71 respectively 70%, as is the open position the mixed air flap 30%. Tells the mixed air flap an opening position of 70%, then the Open position of the fresh air flap 70 and the exhaust damper 71 30% each.

In this way, a certain proportion of sucked air through the recirculation duct 12 again the Supply route. At the same time via the fresh air channel 20 and the fresh air flap 70 of the supply air corresponding proportion of fresh air supplied. This Fresh air proportion is the embodiment in Ventilation case - during office hours - up to 100%. During office hours so is the mixed air flap 72 not usually open, the fresh air flap 70 and the exhaust damper 71 are normally open to 100%. With increased heating demand and a maximum supply P_{TO MAX} decreases the amount of fresh air to approximately 10% off - warming up in the morning -.

When the air conditioning is obtained from the measured room temperature T_{SPACE IS 1}, T_{SPACE IS 2} or T_{SPACE IS N} in the minimum selector 400 in Fig. 2, the lowest value T_{SPACE IS MIN} determined and used to calculate the heating requirements used. For this purpose, the actual temperature T_{SPACE IS MIN} in the Block diagram element 100 from the predetermined (maximum) Desired temperature T_{ROOM DES} (All rooms) subtracted. Due to the so calculated temperature difference T (error) is the temperature control 130 an appropriate control value y 'for the heating valve 170 the heating device 30 is determined in FIG. 1.

The calculated by the controller 120 in FIG. 3, the temperature control Manipulated variable y_R is from the downstream Switching means 125 monitors to a conventional Regulators usual temperature overshoot largely to prevent. In the normal case, as long as T_ROOM_{IS MIN} under T_{ROOM DES} is located, the control device 125, the manipulated variable y_R unchanged as y 'to the heating valve 170 on. but exceeds T_{SPACE IS MIN} the Desired temperature T_{ROOM DES}, Then instead of y_R a much smaller manipulated variable y 'to the heating valve 170 forwarded. The value of the manipulated variable y 'is in this case, the supply air temperature minimum required T_{FOR MIN} sure, which is dependent on the outside temperature T_A, In this manner, in the embodiment a maximum overshoot of the desired temperature of reached only 0.3 ° C, an undershoot find almost as not held.

The monitoring of the output signal y _R the controller 120 is in the embodiment, by a switching device 127 in Fig. 7, and a minimum selection means 128 realized. generates the control means 127 same to the controller 120 a control signal y_S , the assumes a maximum size value, as long as the desired temperature T_{ROOM DES} on the actual temperature T_{SPACE IS MIN}is a down to very low control output signal y_{S MIN}. when the actual temperature exceeds the setpoint.

The control output signal y_{S MIN} the control device 128 is to cut off the undershoot otherwise occur the temperature control function of the outside temperature T_A With the aspirated fresh air is set by the calculating means 129th

The minimum selector 128 selects from the two its disposal manipulated value signals y_R and y_Srespectively the smaller and outputs this as y 'to the Heating valve 170 further. In this manner, a Overshooting the temperature to be controlled as far as possible prevented.

Depending on the temperature of the supply air is the Air flow of supply air 15 via the generated supply pressure P_{TO BE} set. For this, first in a P_{TO TARGET}Value calculating means 200 in Fig. 2 a value P_{TO TARGET} intended for the supply pressure. Of the Relationship between the supply air temperature T_TO and the supply pressure P_{TO TARGET} is shown in FIG. 6a, and for the case that the room temperature T_{sPACE IS}smaller than the target value of the room temperature T_{ROOM DES}is.

Only when the supply air temperature significantly above the setpoint temperature is, in the embodiment at 5 ° C, the target pressure of the air is increased. At an air inlet temperature below this threshold, only the will to Good ventilation necessary volume of air in the air-conditioned Facilities blown.

The connection between the room temperature T_{sPACE IS}and the nominal value of supply pressure P_{TO TARGET} is shown in Fig. 6b reproduced and for the case that the room temperature T_{sPACE IS} greater than the target value of the room temperature T_{ROOM DES}or equal to the target value of the room temperature T_{ROOM DES}is.

With increasing ambient temperature T_{sPACE IS}When the room temperature greater than the target value of the room temperature T_{ROOM DES} is, the supply air temperature T decreases_TO and the Setpoint supply pressure P_{TO TARGET} from its maximum pressure P_{TO TARGET MAX} until his minimum pressure P_{TO TARGET MIN},

The from the P_{TO TARGET}Value computing means 200 in FIG. 2 certain Zuluftsolldruck P_{TO TARGET} is a block diagram element 230 with the supply air actual pressure P_{TO BE}compared. The pressure difference Δ P is the pressure control 250 sent.

The complete pressure control circuit is shown in Fig. 4. The control difference Δ P is the regulator sent 240, of the manipulated variable y_P adjusts. A limit switch 245 monitors the output value y_PSo that a predetermined minimum pressure P_{FOR MIN}Who prescribed a Minimum ventilation volume does not fall below, becomes. The output value y_P'Of the limit switch 245 is the fan 285 in FIG. 4 or 15 in Fig. 1 is controlled, the pressure of the control path 286 generated.

With a corresponding control circuit is through the exhaust air motor 16 in the exhaust duct 11 an underpressure P_FROM generated, the one to maintain a predetermined overpressure in the spaces corresponding air volume again sucks. The regulation of the air motor 16 is further described below.

The tempered supply air in the supply duct 10 is about the Supply air lines 5 for ventilation and heating of all Rooms 1 available. With the help of the throttle 60, 61 the volume of air blown into each room individually and extracted air at the respective actual Heating needs adjusted. For this purpose each the target temperature, the actual temperature, the supply air temperature and the minimum ventilation volume for the setting the throttle used. This control loop, in Fig. 2 as a block diagram element 300 shown, is shown in Fig. 5.

In the block diagram element 310 is the custom Desired temperature T_{SOLL N} with the corresponding actual temperature T_{IS N} compared; the case determined control difference Δ T_N is supplied to the regulator 320th This generated due to the temperature difference Δ T_N of the supply air temperature T_TO and the supply pressure P_TO a control signal y_TN does not fall below a minimum value may, resulting from the current supply air pressure P_TO and the minimum pressure P_{FOR MIN} results. The control signal y_TN . is the throttle valve 330 in Figs. 5 and 60, 61 in Fig. 1 fed. The control system of this individual temperature control loop is a block diagram element represents 340th

The throttles 60, 61 are a function of the in each room set temperature setpoint T_{ROOM DES} the measured in each individual room temperature actual value T_{sPACE IS} the temperature value of the supply air T_TO and as a function of supply pressure P_TOand / or regulated the rotational speed of the supply air.

As stated above, the control circuit ensures the Adjustment of the opening cross section of the throttle valve 60, 61 a specific, depending on the supply pressure resulting minimum opening cross-section which 60, 61 does not fall below when setting the throttle becomes. This minimum opening cross section is adjusted so that each space a given absolute minimum fresh volume is replaced.

The minimum opening area of ​​the throttle 60, 61 is also a function of the opening of the Fresh air damper 70, the air damper 71 and the Mixed air damper 72 set.

In controlled delivery of the supply air and exhaust air the opening positions of the mutually associated Throttle 60, 61 in one room 1 equal.

In the regulation of the exhaust air motor 785 of FIG. 8b or 16 to FIG. 1, the set value for the exhaust air in motor Depending on the outside temperature in the P_{DIFF SOLL}Value calculation means 710 is calculated, wherein this Setpoint a relative to the external pressure P_A dependent on determined by the outside temperature room pressure P_{DIFF SOLL} forms. The setpoint P_{AB SOLL} can also in dependence of the supply air temperature and / or the supply pressure be determined.

The relationship between the outdoor temperature T_A and the target value for the room pressure P_{DIFF SOLL}, which from the difference between the target value of the exhaust pressure P_{AB SOLL} and the external pressure P_A results, is in Fig. 8c reproduced. If the outdoor temperature T_Aexceeds a certain threshold, for example, an outside temperature of - 10 ° C, falls to the setpoint P_{DIFF SOLL} the exhaust motor with outside temperature rises from its maximum P_{DIFF SOLL MAX} up to its minimum P_{DIFF SOLL MIN} with a further limit, for example, at an outside temperature of + 15 ° C. When the outside temperature before or after this by the two limits specified temperature range corresponds to Setpoint of exhaust air motor P_{DIFF SOLL} either the maximum Room differential pressure P_{DIFF SOLL MAX} or the minimum Room differential pressure P_{DIFF SOLL MIN},

The from the P_{DIFF SOLL}Value calculation means 710 in Fig. 8a specific target value of the exhaust air motor P_{DIFF SOLL}is a block diagram element 700 with the space difference pipe pressure P_{DIFF IST} in a room and at more Rooms with the air inlet and outlet channel differential pressure compared. The pressure difference Δ P_DIFF becomes the pressure control 730 supplied.

The complete pressure control circuit is shown in Fig. 8b. The control difference Δ P_DIFF is the regulator 740 sent, the manipulated variable y_{P DIFF} adjusts. If multiple windows open in a Cubicle are, the exhaust fans can be switched off completely - only then a slight overpressure are respected -.

The output value y_{P DIFF} the controller 740 is the exhaust air motor controlled 785.in Fig. 8b and 16 in FIG. 1, generates the pressure of the control path 786th

The actual value for the controller 740 of the air motor 16 or 785 is the room differential pressure P_{DIFF IST} educated, resulting from the difference between the external pressure P_Aand the chamber pressure P_{sPACE IS} = P_{AB IS} results.

The embodiment described can be analogous to the cooling be used.

In an additional control circuit, the humidity regulated in the air-conditioned rooms. It is preferably as relative humidity (in percentage of Vapor pressure measured at full saturation) and expressed, simplified in the following referred to with the symbol F. But it is quite possible, in place of relative humidity, the absolute humidity (in g of water vapor on a m³ Air), the vapor pressure, specific humidity (in g H₂O to 1 kg of moist air) or as a mixture ratio (in g H₂O dry to 1 kg to use air). When using the relative Humidity is the dependence of the saturation limit advantageously integrated into the value. After the VDI ventilation rules should the humidity in winter relative at 20 ° C ambient air temperature from 35 to 70% be humidity in the summer at 22 ° C Raumlüfttemperatur 70%, at 25 ° C 60%.

In the block diagram element 600 in FIG. 2 is the difference of desired humidity F_{AB SOLL} and actual air-humid F_{AB IS} determined, representative of the humidity in the individual rooms in the embodiment the moisture in the air F_FROM measured and adjusted becomes. The calculated humidity difference Δ F_FROM is first a limit switch device supplied 610 the basis of predetermined minimum and maximum Humidity limits F_{AB MIN} and F_{AB MAX} in dependence of the supply and return air temperature prevents in Humidity control at any point in the air circuit the saturation limit is exceeded. Of this Limit switching device 610 will now be corrected Control difference Δ F_FROM'The controller 620 supplied the the humidifier 630 via the control signal y_L controls. This is the humidity of the supply air F_TO set. The controlled system is the block diagram element represents 640th

The second heating device 33 may also be in the heating mode the signal y 'of the first heating device 30 is obtained. but the second heating device 33 serves as a Reheaters essentially for dehumidification. These second heating device 33 is a function of the actual value moisture F_IS regulated for setpoint humidity, wherein with increasing actual value moisture F_IS above the set point humidity F_SHOULD the heat output of the second heating device 33 rises. The increase in heat output the second heating apparatus 33 rises above a predetermined humidity range of ambient humidity F_IS,

This relationship is shown in Fig. 9. At a Room humidity F_IS before this moisture range is the second heating apparatus 33 is not in operation.

At a room moisture F_IS after this moisture range is the second heating device 33 - reheaters - At its maximum performance in operation.

By a control device not shown here ensures that the delivery of the supply air is not increased during the Entfeuchtungsvorganges and only a minimum amount of fresh air is blown.

To better illustrate the control is in following example describes a warm-up operation, as usually occurs in the morning. The on expiry the control block diagram of the elements involved are shown in Fig. 10. On power- the air conditioning apparatus to the actual temperatures all the rooms 1 and the temperature of the intake Fresh air far beyond the target temperature for the spaces 1 lie. Since the temperature of the air is still very low is, more air is not blown into the rooms. For this purpose the supply motor 15 an the minimum fresh air volume corresponding minimum air pressure P_{FOR MIN}generated.

At low outside temperature drops below 16 ° C, the regulator will at startup to a value according to the outside temperature preset, so that the plant at startup no frost disturbance having.

Of the actual temperatures of all rooms to be air conditioned 1 selects the minimum selector 400 the lowest Value and passes it to the block diagram element 100. Here is the error signal Δ T between the set and actual room temperatures formed and the controller 120 and the control device 127 sent. The controller 120 determines a result of Control difference Δ T a manipulated variable y_R, simultaneously is used by the control device 127 a control value y_S certainly, assuming a maximum of great importance, as long as the target temperature is above the actual temperature. From the two manipulated variables y_S and y_R selects the minimum selector 128 from the smaller, at this time the manipulated variable y_R the controller 120, and passes it the heating device 30 further. This warms the flowing through the supply air duct 10 air according on. Thus, the supply air temperature T rises_TO continuous at. From a predetermined temperature threshold the supply air, for example, T_{TO TARGET} + 5 ° C, with further rising supply air temperature and the supply pressure increased since the regulation of supply pressure depending takes place by the temperature of the supply air. The delivery increases and there is a maximum speed Heating instead of all the rooms.

The increased volume of air is not just fresh air, but a part of the exhaust air is recirculated air channel 12 in FIG. 1 fed back to the supply air. On Thus, the rooms 1 and adequately ventilated simultaneously does not have an unnecessary amount of fresh air heated will.

During the morning heating is the proportion of fresh air only - at least - so large, so that the necessary Overpressure is achieved.

Is the heating finished, reduce commercial The manipulated variable y_R unsatisfactory rapidly to an increase in the actual temperatures of Rooms 1 to prevent on the target temperature. That's why decreases the manipulated variable y_S the controller 127 when Exceed the target temperature to a predetermined Minimum value y_{S MIN} from. Now select the minimum selector 128 the value of y_S the control device 127 and outputs it as y 'to the heating device 30 further. Thereafter, the supply air temperature drops again, and after a short time, the spaces only supplied with the minimum fresh air volume is sufficiently heated to a decrease in the actual temperature of the incoming air below the desired temperature of the supply air to prevent. The controller can thus its output slowly shrink.

It now is also the case described, in which only one room to be heated, while already reached the other rooms the setpoint temperature have. From the minimum selector 400 is the selected lowest actual temperature of unheated rooms and routed to the block diagram element 100th by virtue of the deviation will be a manipulated variable y ' adjusted and the supply air temperature and the supply pressure correspondingly increase. But that's not even the rooms are furnished with very warm incoming air, which have already reached the desired temperature, regulates the room temperature control Individual 300 via throttle 60, 61 separate the injected for each room Volume of air. In this way, the throttles 60, 61 of the rooms in which the actual temperature of the Setpoint temperature has been reached, at a minimum cross section closed, which ensures that the Rooms are adequately ventilated. At the same time open with increasing T_TO the throttle valves 60, 61 to be heated of the Space up to 100% and P_DIFF up to 100% to to allow a rapid heating. Only if this compartment has reached its target temperature, provides the air conditioning control again to Mindestbelüftungs- and target temperature retention state.

LIST OF REFERENCE NUMBERS

<dl tsize="8" compact="compact"><dt>1</dt><dd>to its climate control room</dd><dt>5</dt><dd>supply air</dd><dt>6</dt><dd>exhaust pipes</dd><dt>10</dt><dd>supply air duct</dd><dt>11</dt><dd>exhaust duct</dd><dt>12</dt><dd>recirculated air duct</dd><dt>15</dt><dd>Supply air</dd><dt>16</dt><dd>exhaust motor</dd><dt>20</dt><dd>Fresh air channel</dd><dt>21</dt><dd>Exhaust air duct</dd><dt>30</dt><dd>Heating device (preheater)</dd><dt>33</dt><dd>Heating apparatus (reheater)</dd><dt>40</dt><dd>cooler</dd><dt>50</dt><dd>Befeuchtigungseinrichtung</dd><dt>60</dt><dd>throttle</dd><dt>61</dt><dd>throttle</dd><dt>70</dt><dd>Fresh air flap</dd><dt>71</dt><dd>Exhaust air damper</dd><dt>72</dt><dd>Mixed air damper</dd><dt>100</dt><dd>Block diagram element</dd><dt>120</dt><dd>regulator</dd><dt>125</dt><dd>Subordinated controller</dd><dt>127</dt><dd>Switchgear / control device</dd><dt>128</dt><dd>Minimum selector / controller</dd><dt>129</dt><dd>calculating means </dd><dt>130</dt><dd>temperature control</dd><dt>170</dt><dd>heatervalve</dd><dt>200</dt><dd>P_{TO TARGET}Value calculation means</dd><dt>230</dt><dd>Block diagram element</dd><dt>240</dt><dd>pressure regulator</dd><dt>245</dt><dd>limit switches</dd><dt>250</dt><dd>pressure control</dd><dt>285</dt><dd>Supply air</dd><dt>286</dt><dd>controlled system</dd><dt>300</dt><dd>Block diagram element / room temperature control Individual</dd><dt>310</dt><dd>Block diagram element</dd><dt>320</dt><dd>regulator</dd><dt>330</dt><dd>throttle</dd><dt>340</dt><dd>Block diagram element</dd><dt>400</dt><dd>Minimum selector</dd><dt>500</dt><dd>controller</dd><dt>550</dt><dd>louver</dd><dt>600</dt><dd>Block diagram element</dd><dt>610</dt><dd>Limit switching device</dd><dt>620</dt><dd>regulator</dd><dt>630</dt><dd>humidifier</dd><dt>640</dt><dd>Block diagram element</dd><dt>700</dt><dd>Block diagram element</dd><dt>710</dt><dd>P_{DIFF SOLL}Value calculation means</dd><dt>730</dt><dd>pressure control</dd><dt>740</dt><dd>regulator</dd><dt>760</dt><dd>controlled system</dd><dt>785</dt><dd>exhaust motor</dd><dt>786</dt><dd>controlled system</dd><dt>P_FROM</dt><dd>exhaust pressure</dd><dt>P_TO</dt><dd>Supply pressure </dd><dt>P_{TO BE}</dt><dd>Supply air pipe pressure</dd><dt>P_{TO TARGET}</dt><dd>Supply pressure setpoint</dd><dt>P_{FOR MIN}</dt><dd>minimum pressure</dd></dl><dl tsize="13" compact="compact"><dt>T_A</dt><dd>outside temperature</dd><dt>T_{SPACE IS 1}</dt><dd>room temperature</dd><dt>T_{SPACE IS 2}</dt><dd>room temperature</dd><dt>T_{SPACE IS N}</dt><dd>room temperature</dd><dt>T_{SPACE IS MIN}</dt><dd>lowest value</dd><dt>T_{ROOM DES}</dt><dd>(Maximum) setpoint temperature</dd><dt>T_{ROOM DES N}</dt><dd>individual setpoint temperature</dd><dt>T_TO</dt><dd>Supply air</dd><dt>T_{FOR MIN}</dt><dd>minimum allowable supply air temperature</dd><dt>y_V</dt><dd>manipulated variable</dd><dt>y '</dt><dd>manipulated variable</dd><dt>y_R</dt><dd>manipulated variable</dd><dt>y_S</dt><dd>actuating signal</dd><dt>y_{S MIN}</dt><dd>very low output value signal</dd><dt>y_P</dt><dd>manipulated variable</dd><dt>y_{P '}</dt><dd>manipulated variable</dd><dt>y_TN</dt><dd>actuating signal</dd><dt>y_L</dt><dd>control signal</dd></dl><dl tsize="10" compact="compact"><dt>F</dt><dd>relative humidity</dd><dt>F_FROM</dt><dd>Humidity of the exhaust air</dd><dt>F_{AB MIN}</dt><dd>minimum humidity threshold</dd><dt>F_{AB MAX}</dt><dd>maximum humidity limit</dd><dt>F_{AB SOLL}</dt><dd>Target humidity</dd><dt>F_TO</dt><dd>Humidity of the intake air </dd><dt>P_DIFF</dt><dd>Room differential pressure</dd><dt>P_{DIFF IST}</dt><dd>Actual value of room differential pressure</dd><dt>P_{DIFF SOLL}</dt><dd>Setpoint of the room differential pressure</dd></dl><dl tsize="6" compact="compact"><dt>Δ P</dt><dd>pressure difference</dd><dt>Δ T</dt><dd>temperature difference</dd><dt>Δ T_N</dt><dd>control difference</dd><dt>Δ F_FROM</dt><dd>humidity difference</dd><dt>Δ F_FROM'</dt><dd>corrected deviation</dd></dl>