EP2802822B1 - Air-conditioning control method in an air system, and device - Google Patents

Description

The invention relates to technologies in the field of regulated air conditioning in a ventilation system, in which case a predetermined target air condition for air with an initial air condition is characterized by air temperature and air humidity.

background

Air is usually cooled and dehumidified in ventilation systems by means of one or more air coolers through which a coolant flows. The output is regulated either on the air side or on the coolant side using a suitable hydraulic circuit. In the case of hydraulic power control, this is usually achieved by changing the coolant flow while maintaining the coolant flow temperature (quantity-controlled cooling). A control option known from heating technology is used less frequently, in which the coolant flow temperature is regulated by means of admixture from the coolant return (admixed cooling).

There are two different hydraulic circuits for the hydraulic control of the cooling capacity, which also cause different changes in the state of the air as it flows through the heat exchanger (air cooler). On the one hand, it is a system in which the air cooler is provided with a quantity control. When the coolant flow temperature is constant, the amount of coolant supplied to the air cooler is regulated. On the other hand, systems are known in which the air cooler is provided with an admixing control. Here, the flow temperature of the coolant fed into the air cooler is regulated.

With a volume-controlled air cooler, dehumidification always takes place in the case of cooling with a water vapor load above a limit value, which depends, among other things, on the supply temperature of the coolant, since the coolant supply temperature can be assumed to be constant, regardless of the building cooling load. As a result, the surface temperature of the air cooler at the coolant inlet is close to that through the refrigerator provided cold water flow temperature. This flow temperature is usually around 6 ° C in conventional systems. The end point of the change in state of the mixed partial flows of the air is theoretically on the connecting line between the state point of the air flow in front of the cooler and the effective surface temperature of the air cooler. The gradient of the change in state in a so-called Mollier diagram for a given cooler design for each starting point of the moist air depends only on the starting point itself and on the effective surface temperature of the air cooler.

A distinction can be made between two operating modes in this known circuit type. Either the desired degree of dehumidification determines the air outlet temperature from the air cooler, or the necessary cooling determines the degree of dehumidification of the air. The desired end point for temperature and humidity cannot be set precisely with the air cooler alone. In order to achieve a fixed air condition, the air flow after the air cooler must either be heated (dehumidification determines the cooling) or the air flow must be humidified (cooling determines the dehumidification).

With an admixed air cooler, an air flow is cooled completely without dehumidification if the temperature of the cooling medium entering the air cooler does not fall below the dew point temperature of the moist air. Only when the coolant flow temperature is below the dew point temperature of the humid air due to throttling of the coolant return admixture does a condensation of water vapor, i.e. dehumidification, begin for a partial air flow.

Ideally, the result is that with an infinite coolant mass flow, the entire air mass flow must be cooled down to the dew point before the dehumidification process begins. If, according to this idea, water vapor is condensed from the air mass flow, the entire amount of air must be cooled down to the dew point of the desired moisture load, which usually results in subcooling of the air mass flow and is therefore energetically unfavorable. The heating of the supercooled air mass flow required to maintain a desired supply air condition requires additional energy, whereby the economy of an admixed cooler continues to deteriorate.

Each of the two known circuits changes exactly one size of the coolant flow to regulate the power of the air cooler. With the volume-controlled circuit, the mass flow (the quantity) is regulated. In the case of the admixed circuit, the coolant flow temperature is regulated according to the performance requirement. Both known circuits have advantages and disadvantages for achieving a desired air condition with regard to temperature and water vapor loading. In the case of the volume-controlled air cooler, depending on the desired air condition, either reheating the air flow or humidifying the air may be necessary. In the case of the dehumidified dehumidifier, it is almost always necessary to cool deeper than the cooling load requires. In these cases, the operation of an air reheater is absolutely necessary to maintain the desired air condition.

Based on the known devices, there is still a need to optimize the air conditioning process, in particular with regard to energy efficiency.

The document DE 10 2009 007 591 B3 discloses a method for air conditioning by means of an air-conditioning system, in which a predetermined target air condition for air with an outlet air condition, characterized by air humidity and air temperature, is set by cooling and dehumidifying the air with the outlet air condition with the aid of an air cooler, with a coolant supply device for the air cooler a coolant supplied to the air cooler regulates both a coolant mass flow and a coolant inlet temperature in accordance with the initial air condition and the predetermined target air condition when cooling and dehumidifying the air. The document DE 10 2009 007 591 B3 thus discloses a method for air conditioning with the features of the preamble of claim 1 and a device for air conditioning with the features of the preamble of claim 11.

Summary

The object of the invention is therefore to provide a method for regulated air conditioning in an air-conditioning system and a device with which the air conditioning process can be carried out more precisely and in a more efficient manner.

According to one aspect, a method for regulated air conditioning in an air conditioning system is created according to independent claim 1. Furthermore, a device for regulated air conditioning is created according to independent claim 11. Advantageous embodiments of the invention are the subject of dependent subclaims.

The proposed technologies for regulated air conditioning are set up, starting from air which has an initial air state, to set a predetermined target state for the air using the air cooler, which is at least determined by air temperature and humidity is characterized. The initial air state can preferably also be characterized on the basis of air temperature and air humidity.

Air conditioning is used, for example, to optimize indoor air conditioning. In this embodiment, the device for regulated air conditioning can be arranged in a ventilation and air conditioning system.

The temperature and / or the moisture loading of the conditioned air, which characterizes a water vapor loading of the air, can be set by means of rules of the ventilation device or system.

The regulation takes place by means of a coolant supply device which supplies a coolant to one or more air coolers. In the coolant supply device, on the one hand the coolant mass flow is regulated, that is the mass flow with which the coolant flows into the air cooler or air coolers. Furthermore, the coolant supply device has a control for the coolant inlet temperature with which the temperature is set at which the coolant enters the air cooler or air coolers. The coolant mass flow is set using a mass flow setting device. The coolant supply device has a temperature control device for setting the coolant inlet temperature.

In such control processes, a controlled variable, for example the room air humidity and / or the room air temperature, is generally recorded, compared with a reference variable (setpoint) and then influenced in the sense of an adjustment to the reference variable. Provision can be made for a regulation of the mass flow setting device and of the temperature control device to be included both in the process for setting the air temperature of the specified target air state and in the process for setting the air humidity (water vapor or moisture loading) of the specified target air state. This can be done by using a control device which is formed, for example, with several control stages or units, which are implemented in separate or one or more integrated controllers. An integrated controller can depend on one or more Control input variables one or more output variables. To this extent, it provides several control functionalities, each of which can be formed using one or more control levels. In one configuration, controller stages that relate to or are assigned to different target components, for example air temperature or moisture loading of the predetermined target air state, can also be implemented in a common integrated controller. This can then result in several controllers being formed in one integrated controller.

The proposed technology optimizes in particular the target or point accuracy of the regulation of the target air condition. The target air condition can also be in a climate range that is determined by a maximum and a minimum temperature and by a maximum and a minimum air humidity. To set the air temperature of the predetermined target air state, a cooling capacity controller stage can couple to the mass flow setting device and regulate it to set a cooling capacity in order to develop the target air state with regard to its air temperature. By adjusting the coolant mass flow, the cooling capacity can be regulated in order to achieve the desired air temperature for the specified target air condition. In this context, a further cooling capacity controller stage can be provided, which in turn couples to the temperature control device and regulates it for setting the target air state if the regulation of the mass flow setting device by the cooling capacity regulator stage is not sufficient to achieve the desired air temperature of the predetermined target air state. Such a case can occur, for example, in the event of a failure or poor performance of the cooling power regulator stage and / or the mass flow setting device.

Similarly, the control device for setting the air humidity of the predetermined target air state can have an air humidity controller which couples to the temperature control device and regulates it for setting the target air state. An air humidity control stage is used to adjust the moisture content of the air to be conditioned. The proposed control process then provides for the use of a further air humidity control stage, which in turn couples to the mass flow setting device and regulates this for setting the target air state if the regulation of the temperature control device by the air humidity control stage is not sufficient, the predetermined air humidity for the target air state to reach. Such a case can occur, for example, in the event of a failure or poor performance of the air humidity control stage and / or the temperature control device.

In one possible embodiment, the proposed technology provides for a multi-stage control for regulating the specified air temperature of the target air state and / or for setting the specified air humidity of the target air state, in which respectively assigned control devices in the coolant supply device influence the coolant mass flow and the coolant inlet temperature. In the case of regulating the air temperature of the predefined target air state, this is initially done, for example, by regulating the coolant mass flow. If necessary, a control of the coolant inlet temperature is connected. With regard to the setting of the air humidity of the predetermined target air state, the regulation by the air humidity controller with the several controller stages can first be carried out with regard to the coolant inlet temperature by adjusting the temperature control device. If necessary, the coolant mass flow is then influenced via the further humidity control stage.

According to the control mechanism provided, in certain operating situations, control signals can be generated and output by at least two controller stages or units, both for the mass flow setting device and for the temperature control device. For the mass flow setting device, this can be the cooling capacity control stage as well as the further air humidity control stage. For the temperature control device, this can be the air humidity control stage as well as the further cooling capacity control stage. In this embodiment, the control concept can provide for the control variables coolant mass flow and coolant inlet temperature to preferably implement the larger of the two control values. The larger of the control values for the coolant mass flow, which are provided by the cooling capacity control stage and by the further air humidity control stage, are therefore given to the mass flow setting device. Regarding the coolant inlet temperature, the control in this embodiment can be carried out in a comparable manner.

Various control engineering methods can be used to implement the control mechanisms or schemes in the various versions in one or more controllers are used, which are known as such, for example, the use of fuzzy logic.

One aspect can be that the air humidity and the temperature of a climate are regulated by means of two actuators in a hydraulic circuit. These actuators are particularly assigned to the mass flow and temperature of the coolant at the inlet of the cooler.

The control of such a system can take into account at least two control variables and generate at least two control variables. The main parameters are the temperature of the air and the absolute or relative humidity. A controlled variable can be the position of a three-way valve used for admixing, which determines the flow temperature. Another control variable can determine the mass flow, it can be the position of the two-way valve or alternatively the speed of a pump. Such a scheme can be implemented, for example, with several "Single Input Single Output" controllers (SI-SO), each with a command and a control variable. In a so-called decentralized control, a separate SISO controller is assigned to each pair of actuating and controlled variables. In the case of weak coupling between the manipulated variable and controlled variable pairs, this is sufficient; in the case of strong coupling, so-called decoupling controllers can be used. Its main task is to eliminate the influence of the other manipulated variable. A variant for such a control scheme is the use of "multiple input single output" controllers (MISO). Alternatively, the control scheme can be implemented by a single so-called "multiple input multiple output" controller (MIMO). Here, several control variables are included in a controller and several control variables are generated.

The input variables for the control are preferably the air humidity and the temperature. Temperatures from the cooling section of the air cooler can also enter the control device; As extreme values, these are the temperatures of the coolant supply and the coolant return and all temperatures in between. In addition to the valve positions for the admixing and two-way valve, output variables of a controller can be additional or alternatively other variables that can be used for other purposes.

Linear controllers, such as classic PID controllers, can be used as controllers. The controlled system cannot be linearized in all cases, then non-linear controllers can be used. These include, for example, adaptive controllers, fuzzy-based controllers, map-based controllers, predictive controllers, two-point controllers, multi-point controllers and combinations of the controllers mentioned.

Map-based controllers can take complex couplings between several input and output variables into account. Maps that can be used with advantage describe the temperature distribution for the air cooler over the air cooler as a function of the inlet temperature, mass flow and / or the temperature of the air (TIDA). Another characteristic diagram describes the mass flow as a function of the speed of a pump, for example a speed-controlled pump.

Predictive controllers are based on a model that describes the physical relationships of the controlled system or a part of the controlled system. For example, a model of an air cooler can advantageously be used, which describes the relationships between the temperature and humidity of the air entering and leaving the cooler and the temperature of the coolant flow and the coolant mass flow. Another suitable model describes the hydraulic circuit, as the relationship between the temperature of the cold water flow, the temperature of the cold water return, the position of the three-way valve for admixing, the position of the two-way valve).

Such a controller can be implemented, for example, in a compact controller, in a programmable logic controller, in a PC, in an "embedded" PC or in an embedded system. Here, the control device can be implemented in a separate unit, which is used exclusively for the purpose of climate control. The control device can also be installed in an existing controller, such as in the control unit of a speed-controlled pump.

A further development can provide that the cooling capacity regulator stage and the further cooling capacity regulator stage are formed in separately designed cooling capacity regulators. Alternatively, it can be provided that the cooling capacity regulator stage and the further cooling capacity regulator stage are formed in an integrated cooling capacity regulator, which regulates the mass flow setting device and, if necessary, the temperature control device for setting the air temperature of the predetermined target air state. The integrated cooling capacity controller thus implements at least the control function of both the cooling capacity regulator stage, which couples to the mass flow setting device, and the further cooling capacity regulator stage, which couples to the temperature control device. In order to set the predetermined air temperature of the target air state, the coolant mass flow is first regulated by means of access to the mass flow setting device in the various configurations. If this regulation is not sufficient to reach the specified air temperature, the integrated cooling capacity controller then also regulates the temperature control device if necessary, in order to influence the coolant inlet temperature.

In an expedient refinement, it can be provided that the air humidity control stage and the further air humidity control stage are formed in separately designed air humidity controllers. Alternatively, it can be provided that the air humidity controller stage and the further air humidity controller stage are formed in an integrated air humidity controller, which regulates the temperature control device and, if necessary, the mass flow adjustment device for setting the air humidity of the specified target air condition. Comparable to the integrated cooling capacity controller, the integrated air humidity controller implements at least the control function of the air humidity controller stage and the further air humidity controller stage, which couple to the temperature control device or the mass flow adjustment device. In order to set the predetermined air humidity of the target air condition, the integrated air humidity controller in the various configurations regulates the temperature control device in order to initially influence the coolant inlet temperature for the coolant supplied to the air cooler. If this control mechanism is not sufficient to set the specified moisture loading of the target air, the integrated air humidity controller then also regulates the mass flow setting device.

An advantageous embodiment can provide that the temperature control device is formed with an admixing device in which the coolant inlet temperature is achieved by mixing of coolant quantities of different temperature is set. The temperature at which the coolant enters the air cooler is set here by mixing together coolant amounts that have different temperatures. For example, a coolant return admixture can be provided, in which the coolant to be supplied to the air cooler is mixed with coolant from the return line of the air cooler to a controlled extent, that is to say in accordance with the regulation oriented to the target air condition.

A further development preferably provides that the mass flow setting device is formed with an adjustable flow device and the coolant mass flow supplied to the air cooler is regulated by setting the flow device. For example, a controllable two-way valve is used as the flow device. To form the coolant flow in the air cooler, a pump device can be integrated in the coolant supply device. The setting of the coolant mass flow can then be carried out additionally or alternatively by means of speed control of the pump device. In this embodiment, the regulated flow valve can optionally be dispensed with. The setting of the coolant mass flow can then only be carried out using the speed-controlled pump device.

In an advantageous embodiment it can be provided that a dew point control is carried out by limiting the coolant inlet temperature to the dew point temperature of a desired moisture loading of the target air condition. The limitation means that the coolant inlet temperature is not below the dew point temperature. For example, a start temperature for the coolant supply to the air cooler can be regulated in this way. This corresponds to the dew point temperature of a water vapor load, which, for example for reasons of comfort, should at least be maintained in the room for which the air conditioning is carried out with the aid of the system. For a comfort climate task, for example office air conditioning, this can be a coolant inlet temperature of 14 ° C, which corresponds to the dew point temperature of a water vapor / moisture load of 10 g / kg at a total pressure of 1000 hPa. This means that there is no dehumidification for cooling air with a water vapor load of up to 10 g / kg at this coolant inlet temperature.

A further development can provide that the dew point control is carried out by means of a dew point controller which functionally couples to the temperature control device. The dew point controller then serves, for example, to set the coolant inlet temperature described above by regulating the temperature control device.

In an expedient embodiment, it can be provided that the air is both cooled and dehumidified during air conditioning. Using the proposed technologies, different operating modes can be carried out in air conditioning. This includes an air conditioning process that both cools and dehumidifies the air. Alternatively, operating states can be provided in which dehumidification essentially does not take place, ie only cooling takes place, which has already been mentioned above by way of example. In contrast, if the coolant inlet temperature is not below the dew point, dehumidification will not take place.

In connection with the device for controlled air conditioning, the configurations explained above in connection with the method for controlled air conditioning can be provided accordingly. For example, the device can have the integrated cooling capacity controller and / or the integrated air humidity controller. For example, the dew point controller can also be provided in the device for regulated air conditioning.

Description of further exemplary embodiments

Fig. 1

eine schematische Darstellung einer Kaltwasserversorgung für drei lufttechnische Anlagen,

Fig. 2

eine schematische Darstellung der Zustandsänderung von feuchter Luft im Kühlfall in einem vereinfachten Mollier-Diagramm,

Fig. 3

eine schematische Darstellung einer Regelstrategie für eine lufttechnische Vorrichtung zur geregelten Luftkonditionierung im vereinfachten Mollier-Diagramm,

Fig. 4

eine schematische Darstellung einer lufttechnischen Anlage zur Raumluftkonditionierung,

Fig. 5

eine schematische Darstellung einer Vorrichtung zur geregelten Luftkonditionierung mit einem Luftkühler aus der lufttechnischen Anlage in Fig. 4,

Fig. 6

eine schematische Darstellung für Regelausgänge in Abhängigkeit einer Eingangsgröße für eine Temperaturregelung, wobei jeweils das Verhalten eines P-Anteils eines PI- oder PID-Reglers gezeigt ist (P-Regler = Proportionalregler, PI-Regler = Proportional-Integral-Regler, PID-Regler = Proportional-Integral-Differential-Regler),

Fig. 7

eine schematische Darstellung für Regelausgänge in Abhängigkeit von einer Eingangsgröße für eine Feuchteregelung, wobei jeweils das Verhalten des P-Anteils eines PI-oder PID-Reglers gezeigt ist,

Fig. 8

eine schematische Darstellung einer weiteren Vorrichtung zur geregelten Luftkonditionierung mit einem Luftkühler aus der lufttechnischen Anlage in Fig. 4,

Fig. 9

eine schematische Darstellung einer Zuordnung eines Ausgangssignals eines Taupunktreglers zu einem Stellsignals für ein Beimischventil,

Fig. 10

eine schematische Darstellung einer Zuordnung eines Ausgangssignals eines Luftfeuchtereglers zu einem Stellsignals für ein Beimischventil und ein Durchgangsventil beim Entfeuchten,

Fig. 11

eine schematische Darstellung einer Zuordnung eines Ausgangssignals eines Kühlleistungsreglers zu einem Stellsignals für ein Beimischventil und ein Durchgangsventil beim Kühlen,

Fig. 12

eine schematische Darstellung einer anderen Vorrichtung zur geregelten Luftkonditionierung mit einem Luftkühler aus der lufttechnischen Anlage in Fig. 4,

Fig. 13

eine schematische Darstellung einer Anordnung mit einem Primärkreis, einem Sekundärkreis und Verbraucher- oder Versorgerkreisen für eine Wärmeversorgung von Lufterhitzern einer lufttechnischen Anlage, und

Fig. 14

eine schematische Darstellung der Anordnung aus Fig. 13 mit einer Regeleinrichtung für Dreiwegeventile in den Verbraucherkreisen.

Further exemplary embodiments are explained in more detail below with reference to figures of a drawing. Here show:

Fig. 1

a schematic representation of a cold water supply for three ventilation systems,

Fig. 2

1 shows a schematic representation of the change in state of moist air in the cooling case in a simplified Mollier diagram,

Fig. 3

1 shows a schematic representation of a control strategy for a ventilation device for controlled air conditioning in a simplified Mollier diagram,

Fig. 4

a schematic representation of an air conditioning system for air conditioning,

Fig. 5

a schematic representation of a device for controlled air conditioning with an air cooler from the ventilation system in Fig. 4 ,

Fig. 6

a schematic representation for control outputs depending on an input variable for a temperature control, the behavior of a P component of a PI or PID controller is shown (P controller = proportional controller, PI controller = proportional integral controller, PID controller = Proportional-integral-differential controller),

Fig. 7

1 shows a schematic representation for control outputs as a function of an input variable for a humidity control, the behavior of the P component of a PI or PID controller being shown in each case,

Fig. 8

a schematic representation of a further device for controlled air conditioning with an air cooler from the ventilation system in Fig. 4 ,

Fig. 9

1 shows a schematic representation of an assignment of an output signal from a dew point controller to an actuating signal for an admixing valve,

Fig. 10

1 shows a schematic representation of an assignment of an output signal of a humidity controller to an actuating signal for an admixing valve and a two-way valve during dehumidification,

Fig. 11

1 shows a schematic representation of an assignment of an output signal of a cooling capacity controller to an actuating signal for an admixing valve and a two-way valve during cooling,

Fig. 12

a schematic representation of another device for controlled air conditioning with an air cooler from the ventilation system in Fig. 4 ,

Fig. 13

a schematic representation of an arrangement with a primary circuit, a secondary circuit and consumer or supplier circuits for a heat supply of air heaters of an air conditioning system, and

Fig. 14

a schematic representation of the arrangement Fig. 13 with a control device for three-way valves in the consumer circles.

Air coolers in ventilation and air conditioning systems (HVAC systems) are often supplied with cold water as the cooling medium. One or more chillers connected in parallel supply the individual air coolers in a secondary circuit. A typical cold water flow temperature is 6 ° C. The spread between cold water supply and cold water return is often 6K in the design case. A schematic representation of an air-conditioning system with a cold water supply with a chiller in a cold water primary circuit 1 and three air coolers 2, 3, 4 in a cold water secondary circuit 5 is shown in FIG Fig. 1 shown. In the embodiment shown, the primary circuit 1 comprises a chiller 6 and a hydraulic switch 7 connected to it.

The three air coolers 2, 3, 4 each output a stream 8 of conditioned air and couple via a coolant flow 9 and a coolant return 10 to a cold water flow distributor 11 and a cold water return manifold 12. A three-way valve 13 in the coolant return 10 couples to a cold water bypass 14 in the Coolant flow 9.

The output control of the air coolers 2, 3, 4, which are used both for cooling and for dehumidifying the air in the HVAC system, is carried out by changing the coolant mass flow and regulating the coolant inlet temperature. If the coolant inlet temperature remains constant in certain operating situations when the coolant mass flow is changed, this corresponds to a pure quantity control. If, in other special operating situations, the coolant inlet temperature is changed while the coolant mass flow is constant, this is a pure admixing control of the air cooler.

Fig. 2 shows a schematic representation of the change in state of moist air in the cooling case in a simplified Mollier diagram.

When the air passes through the air coolers 2, 3, 4, dehumidification always takes place when the coolant inlet temperature is below the dew point temperature of the air at the cooler inlet. Since, in the case of the volume-controlled operating situation of the air cooler, the coolant inlet temperature, regardless of the cooling load, can be assumed to be close to the cold water inlet temperature provided by the chiller, the air condition at the cooler outlet is theoretically on the connecting line between the air inlet condition (point 1 in Fig. 2 ) and the effective surface temperature of the air cooler (point t _{O, eff} ).

In the case of the admixed operating situation of the air cooler, an air stream, regardless of the cold water temperature, can be cooled completely without dehumidification if the coolant inlet temperature does not fall below the dew point temperature of the moist air due to the addition of return (see. Fig. 2 , Routes 1 - 3). Condensation of water vapor, i.e. dehumidification, only begins at lower coolant inlet temperatures (cf. Fig. 2 , Routes 3 - 4).

In order to cool an air flow of 1 kg / s in the air cooler from the temperature t ₁ to the temperature t ₂ = t ₃ , the specific enthalpy difference (h ₁ - h ₂ ) is removed with the cold water flow in the quantity-controlled air cooler; in the case of the cooler with mixing control, on the other hand, the specific enthalpy difference (h ₁ - h ₃ ). The specific energetic difference between the two changes in the state of the air flow is (h ₃ - h ₂ ). In the event that dehumidification of the air is not necessary, the cooling in the admixed air cooler is therefore significantly more efficient.

If instead of the temperature (t ₂ = t ₃ ) a certain water vapor load of the air (x ₂ = x ₄ ) is to be achieved at the cooler outlet, the volume-controlled operation of the air cooler is more energy efficient. The specific energy saved with this circuit (compared to the admixed air cooler) is characterized by the difference in specific enthalpy (h ₂ - h ₄ ). Point 5 is reached in both circuits with the same coolant mass flow and without addition of return.

Points in Fig. 2 between the two routes (1 - 2 - 5 and 1 - 3 - 4 - 5 in Fig. 2 ) cannot be reached with the operating modes quantity-controlled and admixed-controlled air cooler at a constant temperature on the cold water supply manifold without additional system components. Additional humidification would be necessary for the volume-controlled switching; reheating for the admixed switching.

In order, for example, to achieve comfortable conditions in the room with regard to the room air temperature and the room air humidity, the room ventilation system must bring the air into the room in such a way that the thermal loads and the moisture loads are compensated. For the sake of energy saving, one should try the possibilities that are predetermined by the comfort field, to be used as far as possible. Therefore, in the case of a central European indoor climate, lower indoor air temperatures with lower indoor air humidity should be aimed for in the winter months, while in summer temperatures at the upper edge of the comfort zone together with higher indoor air humidity are sensible from an energetic point of view.

Only the combination of both circuits, i.e. the combination of quantity control and admixing control, - realized, for example, either by connecting two air coolers in series or by integrating both hydraulic circuits on one air cooler - allows each point to be reached in the shaded area in Fig. 2 , which is limited by the two lines of the two conventional circuits. With this integrated circuit, with minimal use of cooling energy, only just as much dehumidification is required as is absolutely necessary to maintain a desired room air condition. Such a circuit can be called, for example, OpDeCoLo (" Optimized Dehumidification Control Loop "). Additional humidification or reheating of the air mass flow to reach any point in the shaded area Fig. 2 is not necessary with this circuit.

In contrast to the conventional air cooler circuits, the OpDeCoLo always regulates both the amount of coolant and its entry temperature into the air cooler for each air cooler. First of all, the coolant inlet temperature is responsible for the dehumidification, i.e. the setting of the air humidity, while the coolant quantity (mass flow) is characteristic for the temperature reduction in the air cooler (cooling capacity). This connection is simplified in Fig. 3 shown.

Fig. 3 shows the control strategy schematically in the simplified Mollier diagram. The vertical (right in Fig. 3 ) represents the limit case of admixed cooling without dehumidification. The coolant flow temperature must not fall below the dew point temperature t _Tau (see lower line of the triangle); the output is regulated by regulating the flow D. The top line of the triangle in Fig. 3 represents the limit of the maximum dehumidification. The coolant flow temperature is adapted to the cold water temperature provided by the chiller; the power regulation takes place by means of Flow control (flow control). Every point on the hatched area between the three legs of the triangle is achieved by a combination of quantity and admixing control. From the vertical, dehumidification is achieved by reducing the coolant flow temperature from the dew point temperature towards the cold water temperature.

Below is with reference to the Fig. 4 and 5 a control mechanism for a device for controlled air conditioning further explained. Fig. 4 shows a schematic representation of a ventilation system 40 (RTL system). This includes a device for regulated air conditioning 41, which in Fig. 5 is shown in detail.

In Fig. 4 the AHU 40 is shown schematically. The air flows are identified as follows: ODA - "Outdoor Air"; RCA - "Recirculation Air"; SUP - "Supply Air"; IDA - "Indoor Air".

In a first step, the control for cooling by means of surface coolers is to be considered separately from the control of the HVAC system 40. Only in a second step is the regulation of the device for regulated air conditioning 41 integrated into the overall regulation of the HVAC system 40.

The regulation of the device for regulated air conditioning 41 is constructed in such a way that the setpoint values for the room air (target air state) preferably represent a most energetically favorable point for cooling, for example in the comfort field. This applies to the combination of room air temperature and room air humidity. This means that both the supply air temperature and the moisture loading of the supplied air are regulated by the appropriate combination of coolant inlet temperature and coolant mass flow. One possibility of regulation is in Fig. 4 shown.

According to Fig. 5 In the device for regulated air conditioning 41, a coolant supply device 43 is connected to an air cooler 42, via which a coolant, in particular water, is supplied to the air cooler 42. In the embodiment shown, the coolant supply device 43 has two valves, namely a two-way valve 44 for regulating the mass flow of the coolant and a mixing valve 45 designed as a three-way valve for regulating the coolant inlet temperature. A pump 46 is arranged in between and can be operated, for example, with a constant delivery head. Three-way valves can be designed as flow combination (admixing) or flow separation valves. Both types can be used, the arrangement of the three-way valve in the circuit changing depending on the choice. Flow combination valves are shown here as examples, which are cheaper than flow isolation valves. However, current isolation valves can also be used without restriction.

Alternatively, in particular for energy reasons, a circuit can be provided in which, instead of the passage valve 44, a pump with regulated speed limits the mass flow (flow). The through valve 44 can then be dispensed with.

In order to carry out a control of the coolant supply device 43 for air conditioning, a cooling capacity control stage 47 couples to the through valve 44, which in the embodiment shown functions as a mass flow setting device. An air humidity control stage 48 couples to the admixing valve 45, which in the embodiment shown functions as a temperature control device for adjusting the coolant inlet temperature . According to Fig. 5 couples a further humidity control stage 49 to the passage valve 44, and a further cooling capacity controller stage 50 couples to the admixing valve 45.

Both the cooling capacity regulator stage 47 and the further cooling capacity regulator stage 50 as well as the air humidity regulator stage 48 and the further air humidity regulator stage 49, which can also be referred to as a corresponding regulator or control unit, differ from the illustration of the exemplary embodiment in FIG Fig. 5 , in one embodiment each implemented in a common controller, namely an (integrated) cooling capacity controller and an (integrated) humidity controller, which is described below with reference to Fig. 8 is further explained.

The control is constructed in one operating mode such that the coolant inlet temperature is set to the dew point temperature of the air state in the air cooler 42 via a dew point controller 51, which couples to the admixing valve 45. Alternatively, the flow temperature be regulated to a fixed value that corresponds to the dew point of the maximum limit.

If the upper limit value of the moisture load in the room (x _{limit, 1} ) is not reached, an attempt is made by limiting the coolant inlet temperature to achieve the required cooling capacity only with "dry cooling" (ie without condensate accumulation) by opening the two-way valve 44. If the "dry cooling" alone is not sufficient to remove the sensitive cooling load despite the fully open through-valve 44, the coolant inlet temperature must be lowered below the dew point of the air by mixing in the return valve 45 in the admixing valve 45. For this purpose, the further cooling capacity control stage 50 acts accordingly on the admixing valve 45. This also causes dehumidification, but the dehumidification effect is minimized because of the then set maximum coolant mass flow.

The control outputs depending on the input variable for the dew point controller 51, the cooling capacity controller stage 47 and the further cooling capacity controller stage 50 are shown in FIG Fig. 6 shown. The control outputs are shown schematically as a function of an input variable for a temperature control, the behavior of a P component of a PI controller being shown in each case.

Fig. 6 shows on the left a schematic representation of an assignment of an output signal of the dew point controller 51 (Y-RE 5) to the control signal at the mixing valve 45 (YDWV). With increasing water vapor loading of the air in the initial state, the dew point of the air rises. In order not to fall below the dew point in the event of undesired dehumidification, the admixing valve 45 is closed when the dew point temperature rises.

Fig. 6 on the right side furthermore shows a schematic illustration for the assignment of the output signals of the cooling capacity control stages 47 (Y-RE 2) and 50 (Y-RE 3) to the control modules 52, 53 (cf. Fig. 8 ) while cooling. Fig. 7 shows a comparable representation for the case of dehumidification, the output signals of the humidity control stages 49 (Y-RE 1) and 48 (Y-RE 4) are shown. YDWV and YDGV denote the control signals to the admixing valve 45 and the two-way valve 44.

In the event that the room air humidity exceeds the limit humidity, a lower admixture is set via the admixing valve 45 under the action of the air humidity control stage 49, and the coolant inlet temperature is thereby lowered. This also changes the cooling capacity, which is normally (the desired target point is within the Fig. 3 hatched area) is compensated by closing the two-way valve 44 under the effect of the cooling capacity control stage 47.

If the target temperature is above that in Fig. 3 hatched area, the air in the air cooler 42 is subcooled. In this case, the further humidity control stage 49 causes the two-way valve 44 to be opened further than is necessary for reaching the target temperature. Reheating is then necessary, as is the case with conventional hydraulic circuits. The process of reheating is not shown here, since reheating is a conventional control task. The control outputs as a function of the input variable for the humidity control stage 48 and the further humidity control stage 49 are in the Fig. 7 shown. Control outputs are shown schematically as a function of an input variable for a humidity control, the behavior of the P component of a PI or PID controller being shown in each case.

Both the temperature control and the control of the dehumidification capacity are designed in two stages: in the temperature control, an attempt is first made to achieve the desired cooling capacity by opening the two-way valve 44. Here, the cooling capacity control stage 47 acts on the passage valve 44. If this is not sufficient, the coolant inlet temperature is reduced by reducing the admixture. For this purpose, the further cooling capacity control stage 50 acts on the admixing valve 45. During dehumidification, an attempt is first made to achieve the desired moisture loading by reducing the coolant inlet temperature. In this case, the air humidity control stage 48 acts on the admixing valve 45. Only when the coolant inlet temperature corresponds to the cold water inlet temperature by avoiding the return flow admixture is the further dehumidification performance achieved by additional mass flow. For this purpose, the further humidity control stage 49 acts on the two-way valve 44.

According to Fig. 5 control modules 52, 53 are provided, which couple to the through valve 44 and the admixing valve 45 and serve a so-called maximum control. In one operating mode, the control modules 52, 53 cause the largest control variable to be applied to the respective valve, for example the larger control signal with respect to the coolant mass flow to the two-way valve 44, if control signals from the cooling capacity control stage 47 and the further air humidity control stage 49 are present, which differ Purpose of mass flows. In the same way, the control module 53 can regulate the regulation of the admixture (the degree of dehumidification) at the admixing valve 45, in which coolant is mixed from the return 54 into the supply 55 in the example shown. Maximum dehumidification is therefore preferably set.

In Fig. 5 the following designations are used: t _TAU - dew point temperature of the air in the initial state; t _VL - coolant flow temperature; x _{limit, 1} - _limit water vapor or limit moisture loading, when exceeded the first control stage is switched; x _{limit, 2} - _limit water vapor or limit moisture loading, when exceeded the second control stage is switched; t _VL - coolant flow temperature; t target _{, 1} - target temperature, when exceeded the first control stage is switched; x _{setpoint, 2} - limit temperature, when exceeded the second control stage is switched; t _IDA - indoor air temperature; and x _IDA - indoor air humidity.

In one embodiment, based on VDI 3525 (from 2007), the exhaust air parameters temperature and air humidity serve as a controlled variable for mixed ventilation systems. For example, with an outdoor temperature of ≤ 22 ° C, the room air should be constant at 22 ° C. As the outside air temperature rises, the setpoint is increased linearly to assume a value of 26 ° C at an outside air temperature of 32 ° C. At higher outside air temperatures, the setpoint must be set to a constant 26 ° C. While the room air temperature is slid over a wide range, in the case of comfort requirements, the humidity only has to be limited with regard to the maximum moisture load. Humidification control is optionally part of the conventional control of the HVAC system.

Fig. 8 shows a schematic representation of a device for controlled air conditioning with an air cooler from the ventilation system in Fig. 4 , unlike the Design in Fig. 5 now the cooling capacity controller stage 47 and the further cooling capacity controller stage 50 as well as the humidity control stage 48 and the further humidity controller stage 49 are each implemented in an integrated cooling capacity controller 80 and an integrated humidity controller 81. For the same characteristics are in Fig. 8 the same reference numerals as in Fig. 5 used. Also in the embodiment in Fig. 8 the control modules 52, 53 are provided, which implement the so-called maximum control, which is described above with reference to FIG Fig. 5 has already been explained. The signals which are obtained from the dew point controller 51 by the control modules 52, 53 are also included in the maximum control.

In one embodiment, the control module 52 can couple to the pump 46 (not shown), whereby the two-way valve 44 can be omitted.

Possible operating situations are described below. In the cooling case, the admixing valve 45 is set for reasons of minimizing the electrical work for a pump drive so that the flow 55 for the air cooler 42 corresponds to the dew point temperature of the air flow. Air cooling thus takes place without dehumidification.

If the admixing valve 45 is in a predetermined position, the air cooler 42 regulates the output when cooling is requested while the pump 46 is running by means of the through valve 44. If the required cooling capacity of the air cooler 42 is not achieved when the through valve 44 is fully open, the temperature of the flow 55 becomes in the following sequence , via which the coolant is supplied, lowered by opening the admixing valve 45. This can lead to undesirable dehumidification of the air flow.

When the through valve 44 is in a predetermined position as a result of the air cooling, the temperature of the flow 55 of the coolant of the air cooler 42 is lowered by adjusting the admixing valve 45 until the desired value for the water vapor loading in the air stream is reached.

Fig. 9 shows a schematic representation of an assignment of an output signal of the dew point controller 51 (Y-RE 3) to the control signal at the mixing valve 45 (YDWV). With increasing water vapor loading of the air in the initial state, the dew point of the air rises. To the In the event of undesirable dehumidification, the admixing valve 45 is closed when the dew point temperature rises.

Fig. 10 shows a schematic representation for the assignment of an output signal of the integrated air humidity controller 81 (Y-RE 2) to the control modules 52, 53 during dehumidification. Fig. 11 shows a comparable representation for the case of cooling, wherein an output signal of the integrated cooling capacity controller 80 (Y-RE 1) is shown. YDWV and YDGV denote the control signals to the admixing valve 45 and the two-way valve 44.

With the help of the proposed control mechanisms, there is a significant advantage in the control with variable temperature of the coolant supply. The chiller does not always have to keep cold water at 6 ° C. If only cold water with a higher temperature is required, chillers with a higher coefficient of performance work more energy-efficiently. This increases the energy saving potential. The signal for the control module 53, which couples to the admixing valve 45, is a measure of the necessary cold water temperature level. In the case of control signals below a limit value, for example 80%, the cold water temperature could be raised. In the case of control signals above this limit, the cold water temperature would have to be reduced again. In cold water systems, as in Fig. 1 shown to supply several air coolers, a maximum selection would again have to be made from the control signals of the respective admixing valves for a decision. The chillers would have to be equipped with a cold water temperature control. This procedure can also be used for air heaters that are almost exclusively admixed (temperature control).

Fig. 12 shows a schematic representation of another device for controlled air conditioning with an air cooler from the ventilation system in Fig. 4 . Here, the two-way valve 44 and the mixing valve 45 couple to a control device 52 ′, which receives a plurality of input variables and uses them to generate control output variables for the two-way valve 44 and the mixing valve 45 for conditioning the target air state. The control device 52 ', as an integrated controller, preferably implements the functionalities for controlling the mass flow and also for tempering in the flow 55.

The proposed circuits are also suitable for the use of variable generator temperatures. The use of a variable flow temperature is provided for the air heating in the air heater.

In connection with ventilation and air conditioning systems (HVAC systems), as explained above, two basic hydraulic circuits for heat exchangers can be distinguished: the quantity-controlled circuit and the admixture-controlled circuit.

The output control of air coolers, which are used both for cooling and for dehumidifying the air in central HVAC systems, is carried out either by changing the cold water mass flow with constant coolant inlet temperature (volume control) or by changing the coolant inlet temperature with constant cold water mass flow (admixed air cooler). The different hydraulic connections of the air cooler result in two different changes in the state of the air as it flows through the air cooler. Air heaters, on the other hand, can be supplied with heating water under admixture control, since the high heating water mass flow ensures uniform heating of the air over the entire cross-section of the heat exchanger. A change in the water vapor loading of the air to be conditioned does not take place in the heating case.

The supply of air conditioning systems in buildings, which are supplied by several such systems, is often carried out centrally. One or more heat generators (boilers, solar collectors, CHP, heat pumps, heat exchangers from district heating, etc.) are hydraulically combined in the primary circuit and provide the heat required by consumers at a specified temperature level.

Fig. 13 shows a schematic representation of an arrangement with a primary circuit 90, a secondary circuit 91 and consumer circuits 92a, 92b, 92c for supplying heat to air heaters of a ventilation system. Heat generators 93, 94 are arranged in the primary circuit 90. The primary circuit 90 couples to a hydraulic switch 95, which is also connected to the secondary circuit 91. The secondary circuit 91 has a heating water supply 96 and a heating water return collector 97. With the heating water flow 96 and the heating water return collector 97, the three supply circuits 92a, 92b, 92c are connected to a three-way valve 98a, 98b, 98c, a pump 99a, 99b, 99c and an air heater 100a, 100b, 100c, which can be assigned to a respective ventilation system.

The separation point between the primary circuit 90 and the secondary circuit 91 is the hydraulic switch 95, which hydraulically decouples the two circuits (cf. Fig. 13 ). The hydraulic switch 95 can also be designed as a reservoir.

The individual consumers are supplied with heating water via a distribution network (secondary circuit 91). The power adjustment takes place in the respective supply circuit 92a, 92b, 92c by admixing the return flow. Chilled water networks are similarly constructed, with chillers based on compression refrigeration and / or absorption or adsorption based being used instead of the heat generators. The air heaters 100a, 100b, 100c would then be replaced by air coolers.

The consumers to be supplied in the secondary circuit 91 have an admixing circuit, that is to say they are operated at a variable temperature with respect to the heating or coolant supply temperature. In addition, the mass flow within the supply circuit 92a, 92b, 92c can also be varied.

In contrast to the thermal supply of static heating surfaces, the temperature level of which is usually dependent on the outside temperature, the principle of constant secondary circuit temperature is used in the conventional supply of heat exchangers in HVAC systems. The advantage of this type of supply is that the control of the heat or "cold" generator can be carried out independently of the mode of operation of the HVAC systems. There is no control technology connection between the producers and the consumers in conventional systems. This makes it possible to separate the entire system into several trades. However, the disadvantages of this control separation between the suppliers and the consumers are that (i) the efficiency for achieving a constant temperature level designed for maximum requirements is not optimal, (ii) the heat losses in the distribution lines are proportional to the temperature difference between the ambient temperature and the generator temperature and (iii) the maximum Required temperature levels often make the integration of regenerative technologies difficult or even impossible.

The efficiency of the generator depending on the temperature level should be illustrated using two examples: the supply of a heating water network by a condensing boiler and the supply of a cold water network by a compression refrigeration machine.

First, consider a condensing boiler as an example. Plants for supplying heating water to air heaters in HVAC systems are usually designed for constant flow temperatures. Given the maximum heating capacity of an air heater, the length of the component depends on the heating medium flow temperature and the temperature spread. The overall length of the air heater also determines the air pressure loss of the component. Since, in addition to the pressure losses in the duct network, the sum of the pressure losses of all components of the HVAC central unit over the duration of the operating hours must be applied by the fan as the delivery pressure, it makes sense to keep the overall lengths of the heat exchangers as low as possible to reduce the air-side pressure losses. The supply temperature level for air heaters is set accordingly high. Typical design temperatures are between 60 ° and 90 ° C. The temperature level is then adjusted to the load on the respective air heater by adding return water.

A heating water supply with a variable secondary circuit flow temperature can open up the possibility that the calorific value of the fossil energy source could be used under certain conditions due to lower target temperatures (partial load range). The condensation of the water vapor generated during the combustion process of fossil fuels increases the efficiency of the boiler, for example in the case of gas by around 10%. In gas boilers with condensing technology, this only happens when the temperature of the combustion gases is below 60 ° C; with oil boilers, even below 50 ° C. Flow temperatures in partial load operation of less than 55 ° C would therefore make energy sense for gas boilers. For certain air conditions, for example when the air is humidified using a spray humidifier, air heating may also be necessary in summer. However, lower than design temperature levels can then also be easily generated using regenerative sources, for example using solar thermal energy.

beschrieben, wobei Q die thermische Kühlenergie der Kompressionskältemaschine und W die dafür aufgewendete Arbeit, zum Beispiel durch den Elektromotor, darstellt. In dieser Gleichung sind die Temperaturen als absolute Temperaturen in Grad Kelvin anzugeben (T = t + 273,15).Another example is a compression refrigerator. The efficiency of the compression refrigeration machine increases with a smaller difference in temperature levels between the evaporator ("refrigeration") and the condenser (heat dissipation to the environment). In the ideal Carnot process, this is due to the coefficient of performance

described, where Q is the thermal cooling energy of the compression refrigerator and W represents the work, for example by the electric motor. In this equation, the temperatures are to be given as absolute temperatures in degrees Kelvin (T = t + 273.15).

If the coolant flow temperature is kept in the area of the dew point of the air in the partial load range, for example to prevent dehumidification of the air to be conditioned in the air cooler, then the cold water flow temperature could be significantly increased.

At an air pressure of 1000 mbar, the dew point temperature for an air condition of 32 ° C and 30% relative humidity (approx. 9 g / kg) is tTau = 12 ° C. If the coolant flow temperature were raised (from typically 6 ° C) to 12 ° C, the evaporator temperature can also be raised by 6 degrees. For an assumed typical evaporator temperature of tVerd. = 0 ° C with a cold water inlet temperature of 6 ° C and a typical condenser temperature in summer for systems without a cooling tower from tKond. = 50 ° C results in a coefficient of performance of εK = 5.46. After raising the evaporator temperature by 6 K, the coefficient of performance is εK = 6.34 while the condenser temperature remains the same; so 16% higher energy efficiency. This means that when the chilled water temperature rises, the ratio of cooling energy to work is improved by 16%. But since the partial load conditions such a drastic increase in the cold water inlet temperature allow only limited, an increase in annual energy efficiency of 10 to 12% should be realistic.

The heat losses in the distribution lines are proportional to the temperature difference between the ambient air and the water. At an ambient temperature of tUm = 20 ° C, lowering the heating water flow temperature from 80 ° C to 50 ° C would result in a reduction in heat loss of 50%. The heat losses of a cold water network decreased at the same ambient temperature when the 6 ° C to 12 ° C increased by over 40%. The proportion of these losses in the total energy consumption depends on the length of the pipes and their insulation. Since the minimum insulation thickness is specified by the legislator, the variable can mainly be seen in the length of the pipe network.

Fig. 14 shows a schematic representation of the arrangement Fig. 13 with a control device 110, which couples to the three-way valves 98a, 98b, 98c and the heat generators 93, 94 and a flow connection 111 of the hydraulic switch 95.

Regardless of whether it is a heating or cold water circuit, the temperature in the secondary circuit 91 is regulated depending on the temperatures or the positions of the three-way valves 98a, 98b, 98c in the supply circuits 92a, 92b, 92c.

In contrast to an outside temperature controlled flow temperature with static heating surfaces, the temperature in the area of the flow distributor is influenced in such a way that the supply circuit with the highest demand is supplied with water of a sufficient temperature level. In order to ensure the controllability of the supply circuits 92a, 92b, 92c, the temperature level of the flow distributor in the heating situation above the level in the supply circuit with the highest demand is selected in the partial load range, the position of the three-way valve for this supply circuit, for example, being a predetermined manipulated variable, for example 90 %, may not exceed. If this limit is exceeded, the setpoint for the flow temperature is increased accordingly. If the manipulated variable falls below a specified limit, for example 80%, the flow temperature is reduced. However, it is also possible to control the temperature in the secondary circuit 91 directly as a function of the temperatures in the supply circuits 92a, 92b, 92c. When cooling, the temperature is in the flow distributor consequently below the lowest temperature in the supply circuits 92a, 92b, 92c.

As an alternative to the execution in Fig. 14 instead of the position of the three-way valve, the manipulated variable of the respective controller (not shown) can be used. The maximum signal then determines the change in the setpoint for the follow-up control of the heat generator or the chiller.

Claims (13)

1. A method for regulated air conditioning in a ventilation system, in which a predetermined target air state, which is characterized at least by air temperature and air humidity, is set for air with an initial air state, in that the air with the initial air state is conditioned with the aid of an air cooler (42), for which, during air conditioning, both a coolant mass flow and a coolant inlet temperature of a coolant supplied to the air cooler (42) are regulated:

   - the coolant being supplied to the air cooler (42) by means of a temperature control device (45), using which the coolant inlet temperature is set, and a mass flow adjustment device (44), using which the coolant mass flow is set, and

   - a regulating device, which couples to the mass flow adjustment device (44) and the temperature control device (45), regulating the mass flow adjustment device (44) and the temperature control device (45) for setting the predetermined target air state characterized in that

   - a temperature of the coolant is regulated in a supply manifold, by means of which the coolant is supplied to the temperature control device (45) and the mass flow adjustment device (44), wherein the regulation of the temperature of the coolant takes place in the supply manifold as a function of

   - a position of the temperature control device (45),

   - a temperature of the temperature control device (45),

   - a manipulated variable of the regulating device for the regulation of the temperature control device (45) or

   - a temperature in a supplier circuit comprising the temperature control device (45) and the mass flow adjustment device (44).
2. The method according to Claim 1, characterized in that the regulating device,

   - for setting the air temperature of the predetermined target air state,

   - regulates the mass flow adjustment device (44) and

   - regulates the temperature control device (45), if the regulation of the mass flow adjustment device (44) does not suffice to reach the air temperature of the predetermined target air state, and/or

   - for setting the air humidity of the predetermined target air state,

   - regulates the temperature control device (45), and

   - regulates the mass flow adjustment device (44), if the regulation of the temperature control device (45) does not suffice to reach the air humidity of the predetermined target air state.
3. The method according to Claim 1 or 2, characterized in that the regulating device,

   - for setting the air temperature of the predetermined target air state, regulates the mass flow adjustment device (44) by means of a cooling-performance regulator stage and the temperature control device (45) by means of a further cooling-performance regulator stage, and/or

   - for setting the air humidity of the predetermined target air state, regulates the temperature control device (45) by means of an air-humidity regulator stage and the mass flow adjustment device (44) by means of a further air-humidity regulator stage.
4. The method according to Claim 3, characterized in that the cooling-performance regulator stage (47) and the further cooling-performance regulator stage (50) are formed in separately realized cooling-performance regulators.
5. The method according to Claim 3 or 4, characterized in that the air-humidity regulator stage (48) and the further air-humidity regulator stage (49) are formed in separately realized air-humidity regulators.
6. The method according to at least one of the preceding claims, characterized in that the temperature control device (45) is formed with a mixing device, in which the coolant inlet temperature is set by means of the mixing of coolant quantities at different temperatures.
7. The method according to at least one of the preceding claims, characterized in that the mass flow adjustment device (44) is formed with an adjustable flow device and the coolant mass flow supplied to the air cooler (42) is regulated by means of the setting of the flow device.
8. The method according to at least one of the preceding claims, characterized in that a dew point regulation is executed in that the coolant inlet temperature is limited to the dew point temperature of a desired moisture content of the target air state.
9. The method according to Claim 8, characterized in that the dew point regulation is executed by means of a dew point regulator (51) which functionally couples to the temperature control device (45).
10. The method according to at least one of the preceding claims, characterized in that during air conditioning the air is both cooled and dehumidified.
11. A device for regulated air conditioning, having:

    - an air cooler (42), which is configured to condition air with an initial air state for setting a predetermined target air state, which is characterized at least by air temperature and air humidity,

    - a coolant supply device, which is suitable for supplying a coolant to the air cooler (42) with a coolant mass flow appropriately and a coolant inlet temperature,

    - a mass flow adjustment device (44), which is formed in the coolant supply device and using which the coolant mass flow is set,

    - a temperature control device (45), which is formed in the coolant supply device and using which the coolant inlet temperature is set,

    - a regulating device, which couples to the mass flow adjustment device (44) and the temperature control device (45), and which is suitable for regulating the mass flow adjustment device (44) and the temperature control device (45) for setting the predetermined target air state, and

    - a supply manifold, by means of which the coolant is supplied to the coolant supply device,

    characterized in that a temperature of the coolant can be regulated in the supply manifold as a function of

    - a position of the temperature control device (45),

    - a temperature of the temperature control device (45),

    - a manipulated variable of the regulating device for the regulation of the temperature control device (45) or

    - a temperature in a supplier circuit comprising the temperature control device (45) and the mass flow adjustment device (44).
12. The device according to Claim 11, characterized in that the regulating device is suitable

    - for setting the air temperature of the predetermined target air state,

    - for regulating the mass flow adjustment device (44), and

    - for regulating the temperature control device (45), if the regulation of the mass flow adjustment device (44) does not suffice to reach the air temperature of the predetermined target air state, and/or

    - for setting the air humidity of the predetermined target air state,

    - for regulating the temperature control device (45), and

    - for regulating the mass flow adjustment device (44), if the regulation of the temperature control device (45) does not suffice to reach the air humidity of the predetermined target air state.
13. The device according to Claim 12, characterized in that the regulating device is formed with a cooling-performance regulator for setting the air temperature of the predetermined target air state and/or with an air-humidity regulator for setting the air humidity of the predetermined target air state.

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