EP2802822A2 - Procédé de conditionnement d'air contrôlé dans une installation de ventilation et dispositif - Google Patents

Procédé de conditionnement d'air contrôlé dans une installation de ventilation et dispositif

Info

Publication number
EP2802822A2
EP2802822A2 EP12821249.5A EP12821249A EP2802822A2 EP 2802822 A2 EP2802822 A2 EP 2802822A2 EP 12821249 A EP12821249 A EP 12821249A EP 2802822 A2 EP2802822 A2 EP 2802822A2
Authority
EP
European Patent Office
Prior art keywords
air
temperature
coolant
control
humidity
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP12821249.5A
Other languages
German (de)
English (en)
Other versions
EP2802822B1 (fr
Inventor
Helmut Feustel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hochschule fuer Technik und Wirtschaft Berlin
Original Assignee
Hochschule fuer Technik und Wirtschaft Berlin
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE201210100304 external-priority patent/DE102012100304A1/de
Application filed by Hochschule fuer Technik und Wirtschaft Berlin filed Critical Hochschule fuer Technik und Wirtschaft Berlin
Publication of EP2802822A2 publication Critical patent/EP2802822A2/fr
Application granted granted Critical
Publication of EP2802822B1 publication Critical patent/EP2802822B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
    • F24F5/0003—Exclusively-fluid systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/46—Improving electric energy efficiency or saving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/06—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the arrangements for the supply of heat-exchange fluid for the subsequent treatment of primary air in the room units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/20—Humidity

Definitions

  • the invention relates to technologies in the field of controlled air conditioning in an air conditioning system, in which case a predetermined and characterized by air temperature and humidity Ziel Kunststoffschreib for air is set with an outlet air condition.
  • the cooling and dehumidification of air in ventilation systems is usually carried out by means of one or more air cooler, which are flowed through by a coolant.
  • the power control takes place either on the air side or on the coolant side by means of a suitable hydraulic circuit.
  • this is usually realized by changing the flow of coolant at a constant coolant flow temperature (volume controlled cooling).
  • volume controlled cooling a control method known from heating technology, in which the coolant flow temperature is regulated by means of admixture from the coolant return (mixture-controlled cooling). This results in the hydraulic control of the cooling power two different hydraulic circuits, which also cause different changes in state of the air when flowing through the heat exchanger (air cooler).
  • the air cooler is provided with a volume control. At constant coolant flow temperature, the amount of coolant supplied to the air cooler is regulated.
  • the air cooler is provided with an admixing. Here, the flow temperature of the coolant fed into the air cooler is controlled.
  • the slope of the change in state in a so-called Mo liier diagram is given a cooler design for each starting point of the humid air only from the starting point itself and the effective surface temperature of the air cooler depends- It can be distinguished in this known circuit type between two modes. 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 can therefore not be precisely adjusted with the air cooler alone. In order to achieve a fixed air condition, the air flow to the air cooler must therefore either be heated (dehumidification determines the cooling), or the air flow must be moistened (cooling determines the dehumidification).
  • a mixed-flow air cooler cools an air stream completely without dehumidification if the inlet temperature of the cooling medium into the air cooler does not fall below the dew point temperature of the moist air. Only when the coolant flow temperature due to throttling of the coolant return admixture is below the dew point temperature of the moist air, is a condensation of water vapor, ie a dehumidification, for a partial air flow. Ideally, with infinite coolant mass flow, the entire air mass flow must be cooled down to the dew point before the dehumidification process even starts.
  • Each of the two known circuits alters exactly one size of the coolant flow for the power control of the air cooler.
  • the mass flow (the quantity) is regulated.
  • the coolant flow temperature is controlled according to the power requirement.
  • both known circuits have advantages and disadvantages.
  • a reheating of the air flow may be necessary, or an air humidification.
  • the mixture-controlled air cooler must almost always be cooled lower than the cooling load requires. The operation of an air reheater is therefore imperative in these cases to obtain the desired air condition.
  • the object of the invention is therefore to provide a method for controlled air conditioning in an air conditioning system and a device with which the process of air conditioning is targeted and more efficient manner executable.
  • a method for controlled air conditioning in an air conditioning system according to the independent claim 1 is provided.
  • a device for controlled air conditioning according to the independent claim 11 is provided.
  • Advantageous embodiments of the invention are the subject of dependent subclaims.
  • the proposed controlled air conditioning technologies are arranged to set, from air having an outlet air condition, a predetermined target air condition using the air cooler which is at least air-cooled. Temperature and humidity is characterized.
  • the outlet air condition is preferably also characterized by air temperature and humidity.
  • the air conditioning serves, for example, an optimized room air conditioning.
  • the device for controlled air conditioning can be arranged in a ventilation and air conditioning system.
  • the temperature and / or the moisture content of the conditioned air which characterizes a water vapor loading of the air, can be adjusted 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.
  • the coolant supply means on the one hand, the coolant mass flow is regulated, that is to say the mass flow with which the coolant flows into the air cooler or coolers.
  • the coolant supply device can have a regulation for the coolant inlet temperature with which the temperature with which the coolant enters the air cooler (s) is set.
  • the adjustment of the coolant mass flow takes place by means of a mass flow adjustment device.
  • the coolant supply device can have a tempering device.
  • Regge generally a controlled variable, so for example, the room air humidity and / or the room air temperature detected, compared with a reference variable (setpoint) and then influenced in terms of an approximation to the reference variable.
  • a controlled variable so for example, the room air humidity and / or the room air temperature detected, compared with a reference variable (setpoint) and then influenced in terms of an approximation to the reference variable.
  • a control of the mass flow adjuster and the tempering is included.
  • An integrated controller can depend on one or more control one or more output variables. In that regard, he provides several control functions that can be formed each with the help of one or more control levels.
  • controller stages which relate to or are associated with different target components, ie, for example, air temperature or moisture charge of the predetermined target air condition can also be implemented in a common integrated controller. This can then lead to several controllers being formed in an integrated controller.
  • the target or point accuracy of the regulation of the target air condition is optimized.
  • the target air condition can also be in a climate range, which is determined by a maximum and a minimum temperature and by a maximum and a minimum humidity.
  • a cooling power regulator stage may couple to the mass flow adjuster and regulate it to adjust a cooling capacity to form the target air condition with respect to its air temperature.
  • a further cooling power regulator stage which in turn couples to the temperature control and then controls this for setting the target air condition when the regulation of the mass flow setting by the cooling power regulator stage is not sufficient to achieve the desired air temperature of the predetermined target air condition.
  • the control device for adjusting the humidity of the predetermined Ziel KunststoffSches have a humidifier, which couples to the temperature control and regulates these for setting the target air condition.
  • An air humidity regulator level adjusts the moisture content of the air to be conditioned.
  • the proposed control process then provides in one embodiment the use of a further air humidity regulator stage, which in turn couples to the mass flow setting device and regulates this for setting the target air condition, if the regulation of the temperature control unit by the air humidity control stage is insufficient to set the predefined air humidity for the target air supply. stood to reach. Such a case may occur, for example, in the event of a failure or poor performance of the humidity regulator stage and / or the tempering device.
  • the proposed technology provides in a possible embodiment for adjusting the predetermined air temperature of the target air condition and / or for setting the predetermined air humidity of the target air condition, a multi-stage control in which each associated control devices in the coolant supply to the coolant mass flow and the coolant inlet temperature influence.
  • a control of the coolant inlet temperature downstream the control by the air humidity regulator with the several control stages can first be carried out with regard to the coolant inlet temperature by adjusting the tempering device. If necessary, the coolant mass flow is then influenced by the further air humidity regulator stage.
  • control signals can be generated and output for at least two controller stages or units for the mass flow setting device as well as for the tempering device in certain operating situations.
  • these may be the cooling output regulator stage as well as the further humidity regulator stage.
  • the tempering this may be the humidity regulator level and the other cooling power regulator stage.
  • the control concept can provide for the control variables coolant mass flow and coolant inlet temperature preferably to implement the respective larger of the two control values. It is the Massenstromeinstell issued so given the larger of the control values for the coolant mass flow, which are provided by thede elaboratesreglerski and the other air humidity control stage. With regard to the coolant inlet temperature, the control can be carried out in a comparable manner in this embodiment.
  • various control engineering techniques which are known as such, for example, the use of fuzzy logic.
  • One aspect may be that the humidity and the temperature of a climate are controlled by means of two actuators in a hydraulic circuit. These actuators are in particular assigned to the mass flow and temperature of the coolant at the inlet of the radiator.
  • control of such a system can take into account at least two reference variables and generate at least two controlled variables.
  • reference values are the temperature of the air and the absolute or relative humidity.
  • a controlled variable may be the position of a used for admixing three-way valve, which determines the flow temperature.
  • Another controlled variable may determine the mass flow, it may be the position of the passage valve or, alternatively, the speed of a pump.
  • Such a scheme can be implemented, for example, with a plurality of Ringle Input Single Output Controllers (SI-SO), each of which has a control variable and a controlled variable If there is weak coupling between the manipulated variable and controlled variable pairs, this is sufficient for strong coupling, so-called decoupling regulators can be used.Their task is in particular to eliminate the influence of the other manipulated variable.
  • SI-SO Ringle Input Single Output Controller
  • the control scheme can be implemented by a single so-called Multiple Input Multiple Output (MIMO) controller. In this case, a number of reference variables enter a controller and several controlled variables are generated.
  • MIMO Multiple Input Multiple Output
  • Input variables in the control are preferably the humidity and the temperature. In the control device but can also enter temperatures from the cooling section of the air cooler; these are extreme temperatures, the temperatures of the coolant flow and the cooling medium return and all temperatures in between.
  • Output variables of a controller can be supplemental or alternatively also other sizes in addition to the valve positions for mixing and through valve, which can be used elsewhere.
  • Linear controllers can be used as controllers, such as classic PID controllers. Not in all cases is the controlled system linearizable, then non-linear controllers can be used. These include, for example, adaptive controllers, fuzzy-based controllers, map-based controllers, predictive controllers, two-point controllers, multipoint controllers and combinations of the aforementioned controllers.
  • Map-based controllers can take into account complex couplings between several input and output variables. Characteristic maps which can be used with advantage describe for the air cooler the temperature distribution over the air cooler as a function of feed temperature, mass flow and / or the temperature of the air (TIDA). Another map describes the mass flow, for example, depending on the speed of a pump, such as a variable speed pump. Predictive controller is based on a model that describes the physical relationships of the controlled system or part of the controlled system.
  • a model of an air cooler can be used, which describes the relationships between the temperature and humidity of the air entering the air cooler and exiting 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 feed, the temperature of the cold water return, the position of the three-way valve for admixture, the position of the passage valve).
  • a controller can be implemented, for example, in a compact controller, in a programmable controller, in a PC, an "embedded" PC or in an embedded system, where the controller can be implemented in a separate unit dedicated solely to the purpose of climate control
  • the control device can also be installed in an existing controller, such as in the control unit of a variable speed pump.
  • a further development can provide that the cooling power regulator stage and the further cooling power regulator stage are formed in separately executed cooling power regulators.
  • the cooling power regulator stage and the further cooling power regulator stage are formed in an integrated cooling power regulator, which regulates the mass flow setting device and, if necessary, the tempering device for adjusting the air temperature of the predetermined target air condition.
  • the integrated cooling power controller thus implements at least the control function of both the cooling power regulator stage, which couples to the mass flow adjustment, as well as the other cooling power regulator stage, which couples to the temperature control.
  • the coolant mass flow is initially regulated by means of access to the mass flow setting device in the various embodiments. If this regulation is not sufficient to reach the specified air temperature, the integrated cooling power controller then regulates the tempering device, if necessary, in order to influence the coolant inlet temperature.
  • the air humidity control stage and the further air humidity control stage are formed in separately executed humidity regulators.
  • the humidity regulator stage and the further humidity regulator level are formed in an integrated air humidity controller which regulates the temperature control device and, if necessary, the mass flow setting device for adjusting the air humidity of the predetermined target air condition.
  • the integrated air humidity controller implements at least the control function of the air humidity control stage as well as of the further air humidity control stage which couple to the tempering device or the mass flow adjustment device.
  • the integrated air humidity controller in the various embodiments controls the tempering device so as 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 humidity load of the target air, then the integrated air humidity controller additionally regulates the mass flow setting device.
  • the tempering device is formed with an admixing device, in which the coolant inlet temperature by means of Mi see set of coolant amounts of different temperature.
  • the temperature at which the coolant enters the air cooler is adjusted by mixing quantities of coolant which have different temperatures.
  • a coolant return admixture can be provided, in which the coolant to be supplied to the air cooler is mixed in a controlled manner, that is to say in accordance with the control of the target air condition, with coolant from the return flow of the air cooler.
  • the mass flow setting device is formed with an adjustable flow-through device and the coolant mass flow supplied to the air cooler is regulated by means of adjusting the flow-through device.
  • a flow-through device for example, an adjustable through-valve will be used.
  • a pump device can be integrated into the coolant supply device. The adjustment 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 can optionally be dispensed with the controlled flow valve. The adjustment of the coolant mass flow can then be carried out exclusively using the variable-speed pumping device.
  • a dew point control is performed by limiting the coolant inlet temperature to the dew point temperature of a desired moisture loading of the target air condition.
  • the limitation causes the coolant inlet temperature is not below the dew point temperature.
  • this can be used to control a starting temperature for the coolant inlet of the air cooler. This corresponds to the dew point temperature of a water vapor load, which is to be maintained, for example, for reasons of comfort in the room for which the air conditioning is carried out with the aid of the system, at least.
  • this may be a coolant inlet temperature of 14 ° C, which at a total pressure of 1000 hPa corresponds to the dew point temperature of a water vapor / moisture loading of 10 g / kg.
  • the dew point control is carried out by means of a dew point controller, which functionally couples to the tempering device. The dew point controller then serves, for example, to adjust the coolant inlet temperature described above by means of regulation of the tempering device.
  • the air is both cooled and dehumidified during air conditioning.
  • the proposed technologies allow different operating modes to be performed in air conditioning. This includes a process for air conditioning in which the air is both cooled and dehumidified.
  • operating states may be provided in which dehumidification is substantially eliminated, ie only cooling takes place, which has already been mentioned above by way of example. If the coolant inlet temperature is not below the dew point, on the other hand is not dehumidified.
  • the device may have the integrated cooling power controller and / or the integrated air humidity controller.
  • the dew point regulator may be provided in the apparatus for controlled air conditioning.
  • 1 is a schematic representation of a cold water supply for three ventilation systems
  • 3 is a schematic representation of a control strategy for a ventilation apparatus for controlled air conditioning in the simplified Mollier diagram
  • 4 is a schematic representation of an air conditioning system for Jardinluftkonditio- n ist
  • FIG. 5 is a schematic representation of a device for controlled air conditioning with an air cooler from the ventilation system in Fig. 4,
  • FIG. 7 shows a schematic representation of control outputs as a function of an input variable for a humidity control, wherein the behavior of the P component of a PI or PID controller is shown in each case,
  • FIG. 8 is a schematic representation of another device for controlled air conditioning with an air cooler from the ventilation system in Fig. 4,
  • FIG. 9 is a schematic representation of an assignment of an output signal of a dew point regulator to a control signal for a mixing valve
  • FIG. 10 is a schematic representation of an assignment of an output signal of a humidity controller to a control signal for an admixing valve and a through valve during dehumidification
  • 11 is a schematic representation of an assignment of an output signal of a cooling capacity regulator to a control signal for a mixing valve and a through valve during cooling
  • FIG. 12 is a schematic representation of another device for controlled air conditioning with an air cooler from the ventilation system in Fig. 4,
  • Fig. 13 is 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 an air conditioning system, and
  • Fig. 14 is a schematic representation of the arrangement of Fig. 13 with a control device for three-way valves in the consumer circuits.
  • Air coolers in ventilation and air conditioning systems are often supplied with cold water as the cooling medium.
  • One or more parallel chillers supply the individual air coolers of a secondary circuit.
  • a typical cold water inlet temperature at 6 ° C. The spread between cold water feed and cold water return is often 6K in the design case.
  • a schematic representation of a ventilation system with a cold water supply with a refrigerator 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. 1.
  • the primary circuit 1 comprises in the illustrated embodiment a chiller 6 and a hydraulic switch 7 connected thereto.
  • the three air coolers 2, 3, 4 each emit 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 collector 12.
  • a three-way valve 13 in the coolant center 10 returns to a cold water bypass 14 in the coolant flow 9.
  • Fig. 2 shows a schematic representation of the change in state of moist air in the cooling case in a simplified Mollier diagram.
  • Points lying in FIG. 2 between the two sections (1 - 2 - 5 and 1 - 3 - 4 - 5 in FIG. 2) are with the operating modes quantity-controlled and mixed-controlled air cooler at the same temperature at the cold water supply manifold without additional system components not available.
  • quantity-controlled circuit an additional humidification would be necessary for this; for the derischgeregelte circuit reheating.
  • the ventilation and air conditioning system In order to achieve comfortable conditions in the room, for example, with regard to the room air temperature and the room air humidity, the ventilation and air conditioning system must introduce the air into the room in such a way that the thermal loads and moisture loads are compensated. For the sake of energy saving should be tried, the possibilities that are given by the comfort field to exhaust as possible. For this reason, in the mid-European indoor climate, lower indoor air temperatures should be aimed at at lower humidities in the winter months, while in summer preferably temperatures at the upper edge of the comfort area together with higher room air humidities make sense from an energy point of view.
  • the OpDeCoLo always regulates both the coolant quantity and its inlet temperature into the air cooler for each air cooler.
  • the coolant inlet temperature for dehumidification ie the adjustment of the air humidity
  • the coolant quantity (mass flow) is characteristic of the temperature reduction in the air cooler (cooling capacity). This relationship is shown in simplified form in FIG.
  • Fig. 3 shows schematically the control strategy in the simplified Mollier diagram.
  • the vertical (on the right in FIG. 3) represents the limiting case of a demix-controlled cooling without dehumidification.
  • the coolant flow temperature must not fall below the dew point temperature rough (see lower line of the triangle); the power control takes place by means of regulation of the flow D.
  • the upper line of the triangle in FIG. 3 represents the limiting case of maximum dehumidification.
  • the coolant flow temperature is adapted to the cold water temperature provided by the cooling machine; the power regulation is carried out flow control (volume control).
  • Each point on the hatched area between the three legs of the triangle is achieved by a combination of quantity and mixing control. From the vertical dehumidification is thus achieved by reducing the coolant flow temperature from the level of dew point in the direction of the cold water temperature out.
  • FIG. 4 shows a schematic representation of a ventilation system 40 (RTL system). This comprises a device for controlled air conditioning 41, which is shown in Fig. 5 in detail.
  • the RLT system 40 is shown schematically.
  • the air flows are marked as follows: ODA - "Outdoor Air”; RCA - "Recirculation Air”; SUP - "Supply Air”; IDA - "Indoor Air”.
  • the regulation for the cooling by means of surface coolers is to be considered separately from the regulation of the air conditioning system 40. Only in a second step, the control of the device for controlled air conditioning 41 is integrated into the overall control of the air conditioning system 40.
  • the regulation of the device for controlled air conditioning 41 is constructed such that the setpoint values of the room air (target air condition) preferably represent a respectively energetically most favorable point for the cooling, for example in the comfort field. This applies to the combination of room air temperature and room humidity. This means that both the supply air temperature and the moisture content of the supplied air are controlled by the appropriate combination of coolant inlet temperature and coolant mass flow.
  • a control option is shown in Fig. 4.
  • a coolant supply means 43 is connected, via which the air cooler 42, a coolant is supplied, in particular water.
  • the coolant supply device 43 has two valves, namely a through-valve 44 for controlling the mass flow of the coolant and a mixing valve 45 designed as a three-way valve for controlling the coolant inlet temperature.
  • a pump 46 is arranged, which is operable, for example, with a constant delivery.
  • Three-way valves may be designed as a stream merging (mixing) or flow separation valves. Both types can be used, with the arrangement of the three-way valve in the circuit varying as desired.
  • power union valves are shown, which are cheaper than power isolation valves. But also power isolation valves can be used without restriction.
  • a circuit may be provided in which instead of the passage valve 44, a pump with a controlled speed limits the mass flow (flow). On the passage valve 44 can then be dispensed with.
  • a cooling power regulator stage 47 is coupled to the through-valve 44, which in the embodiment shown acts as a mass flow adjusting device.
  • An air humidity control stage 48 couples to the mixing valve 45, which in the embodiment shown acts as a temperature control device Adjusting the coolant inlet temperature functions.
  • another air humidity control stage 49 is coupled to the through-valve 44, and another cooling power regulator stage 50 couples to the mixing valve 45.
  • Both the cooling power regulator stage 47 and the further cooling power regulator stage 50 and the humidity regulator stage 48 and the further humidity regulator stage 49 which can also be referred to as respective regulator or control unit, are, in a departure from the representation of the embodiment in FIG implemented in a common controller, namely a (integrated) cooling capacity controller and an (integrated) humidistat, which will be further explained below with reference to FIG.
  • the control is configured in an operating mode such that the coolant inlet temperature is set to the dew point temperature of the air condition in the air cooler 42 via a dew point regulator 51, which couples to the mixing valve 45.
  • the flow temperature be regulated to a fixed value, which corresponds to the dew point of the maximum limit value.
  • the control outputs as a function of the input variable for the dew point controller 51, the cooling power regulator stage 47 and the other cooling power regulator stage 50 are shown in FIG. 6.
  • the control outputs are shown schematically as a function of an input variable for a temperature control, wherein in each case the behavior of a P component of a PI controller is shown.
  • Fig. 6 shows on the left side a schematic representation of an assignment of an output signal of the dew point regulator 51 (Y-RE 5) to the control signal at the mixing valve 45 (YDWV).
  • FIG. 6 also shows, on the right-hand side, a schematic representation for the assignment of the output signals of the cooling-power regulator stages 47 (Y-RE 2) and 50 (Y-RE 3) to the control modules 52, 53 (see FIG. Fig. 7 shows a similar representation for the case of dehumidification, wherein the output signals of the humidifier stages 49 (Y-RE 1) and 48 (Y-RE 4) are shown.
  • YDWV and YDGV denote the control signals to the mixing valve 45 and the passage valve 44.
  • a lower admixture is adjusted via the admixing valve 45 under the action of the humidity regulator stage 49, thereby lowering the coolant inlet temperature.
  • This also changes the cooling capacity, which is normally compensated (desired target point lies within the hatched area shown in FIG. 3) by closing the passage valve 44 under the effect of the cooling power regulator stage 47.
  • the control outputs as a function of the input variable for the humidity regulator stage 48 and the further humidity regulator stage 49 are shown in FIG. 7. Control outputs are shown schematically as a function of an input variable for a humidity control, wherein the behavior of the P component of a PI or PID controller is shown in each case.
  • Both the temperature control and the control of the dehumidification performance are applied in two stages: in the temperature control is first trying to achieve the desired cooling capacity through the opening of the passage valve 44.
  • the cooling power regulator stage 47 acts on the passage valve 44. If this is insufficient, the coolant inlet temperature is lowered by reducing the admixture.
  • the further cooling power regulator stage 50 acts on the admixing valve 45.
  • the humidity regulator stage 48 acts on the mixing valve 45. Only when the coolant inlet temperature by avoiding the Gebauerischung that corresponds to the cold water inlet temperature, the further dehumidification performance is achieved by additional mass flow.
  • control modules 52, 53 are provided, which couple to the through-valve 44 and the mixing valve 45 and serve a so-called maximum control.
  • the control modules 52, 53 effect in an operating mode that the largest control variable is applied to the respective valve, that is, for example, the larger actuating signal with respect to the coolant mass flow to the through valve 44, if there are actuating signals from the cooling power regulator stage 47 and the further air humidity control stage 49, the purpose of which are the different mass flows.
  • control module 53 can regulate the control of the admixture (the degree of dehumidification) at the mixing valve 45, in which, in the example shown, coolant from the return 54 is mixed into the feed 55. It is therefore preferred to set a maximum dehumidification.
  • t T Au - dew point temperature of the air in the initial state tvL - coolant flow temperature
  • xorenz, ⁇ - limiting water vapor or boundary moisture loading exceeding which the first control stage is switched
  • tvL - coolant flow temperature t soll , 1 - set temperature, when exceeded, the first control stage is switched
  • x soll , 2 - limit temperature above which the second control stage is switched ti D A - room air temperature; and XIDA - room humidity.
  • the exhaust air parameters temperature and humidity are used as the controlled variable for mixed ventilation systems.
  • the room air should be constant at 22 ° C.
  • the set point is raised linearly to reach a value of 26 ° C at an outdoor air temperature of 32 ° C.
  • the setpoint must be set to a constant 26 ° C.
  • the humidity in the case of comfort requirements must be limited only in terms of the maximum moisture content.
  • a humidification control is optionally part of the conventional RLT system control.
  • FIG. 8 shows a schematic representation of a device for regulated air conditioning with an air cooler from the ventilation system in FIG. 4, wherein, in contrast to FIG 5, the cooling power regulator stage 47 and the further cooling power regulator stage 50 as well as the humidity regulator stage 48 and the further humidity regulator stage 49 are each implemented in an integrated cooling power regulator 80 and an integrated air humidity regulator 81.
  • the same reference numerals as in Fig. 5 are used in Fig. 8.
  • the control modules 52, 53 are provided, which implement the so-called maximum control, which has already been explained above with reference to FIG. Included in the maximum control are also the signals which are obtained by the control modules 52, 53 from the dew point controller 51.
  • the control module 52 may couple to the pump 46 (not shown) with the passage valve 44 omitted.
  • the mixing 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.
  • the air cooler 42 is controlled in cooling mode when the pump 46 is running by means of the through-valve 44. Should the required cooling capacity of the air cooler 42 not be achieved when the through-valve 44 is fully open, the temperature of the forward flow 55 in the following sequence will be 55 , via which the coolant is supplied, lowered by opening the mixing valve 45. This can lead to unwanted dehumidification of the air flow.
  • the temperature of the flow 55 of the coolant of the air cooler 42 by adjusting the mixing valve 45 is lowered until the desired value of the water vapor load in the air flow is reached.
  • FIG 9 shows a schematic representation of an assignment of an output signal of the dew point regulator 51 (Y-RE 3) to the actuating signal at the admixing valve 45 (YDWV).
  • Fig. 10 shows a schematic representation for the assignment of an output signal of the integrated humidity regulator 81 (Y-RE 2) to the control modules 52, 53 during dehumidification.
  • Fig. 11 is a comparative illustration in the case of cooling showing an output of the integrated cooling capacity controller 80 (Y-RE 1).
  • YDWV and YDGV denote the control signals to the mixing valve 45 and the flow-through valve 44.
  • a measure of the necessary cold water temperature level is, for example, the signal on the control module 53, which couples to the mixing valve 45. With control signals below a limit value, for example 80%, the chilled water temperature could be raised. For control signals above this limit, the cold water temperature would have to be lowered again. In the case of cold water systems which supply a plurality of air coolers, as shown in FIG. 1, a maximum selection would again have to be made from the actuating signals of the respective mixing valves for a decision. The chillers would be equipped accordingly with a cold water temperature control. This procedure can also be used for air heaters that are almost exclusively mixed-controlled (temperature control).
  • FIG. 12 shows a schematic representation of another device for regulated air conditioning with an air cooler from the ventilation system in FIG. 4.
  • the through-valve 44 and the mixing valve 45 couple to a control device 52 ', which receives a plurality of input variables and from this for conditioning of the target air condition control output variables for both the through valve 44 and the mixing valve 45 is generated.
  • the control device 52 ' implemented as an integrated controller preferably the functionalities for controlling the mass flow as well as for the temperature control in the flow 55th
  • the proposed circuits are also suitable for the application of variable generator temperatures. For the air heating in the air heater, the use of a variable flow temperature is provided.
  • two basic hydraulic circuits for heat exchangers can be distinguished in connection with ventilation and air conditioning systems (RLT systems): the quantity-controlled circuit and the mixed-control circuit.
  • Air coolers which are used both for cooling and for dehumidifying the air in centralized air conditioning systems, takes place either by changing the cold water mass flow at a constant coolant inlet temperature (volume control) or by changing the coolant inlet temperature at constant cold water mass flow (mixed air cooler) ,
  • volume control volume control
  • mixed air cooler mixed air cooler
  • Air heaters can be supplied with heating water with mixed 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 case of heating.
  • HVAC systems in buildings which are supplied by several such systems, is often done centrally.
  • One or more heat generators (boilers, solar collectors, cogeneration, heat pumps, heat exchangers of district heating, etc.) are hydraulically combined in the primary circuit and provide the heat required by the consumers at a given 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 a heat supply of air heaters of an air conditioning system.
  • heat generator 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 Schumachervorlauf 96 and a Schuzierschenmaschinesammler 97.
  • the three supplier circuits 92a, 92b, 92c connected to a three-way valve 98a, 98b, 98c, a pump 99a, 99b, 99c and an air heater 100a, 100b, 100c, which may be associated with a respective ventilation system.
  • a three-way valve 98a, 98b, 98c a pump 99a, 99b, 99c and an air heater 100a, 100b, 100c, which may be associated with a respective ventilation system.
  • the hydraulic switch 95 Separation point between the primary circuit 90 and the secondary circuit 91 is the hydraulic switch 95, which hydraulically decouples the two circles (see Fig. 13).
  • the hydraulic switch 95 can also be designed as a storage.
  • a distribution network (secondary circuit 91) supplies the individual consumers with heating water.
  • the power adjustment takes place in the respective supplier circuit 92a, 92b, 92c by return addition.
  • cold water networks are constructed, but instead of the heat generator chillers on compression refrigeration and / or absorption or adsorption are used.
  • 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, ie they are operated with a variable temperature with respect to the heating or coolant feed temperature.
  • the mass flow within the supply circuit 92a, 92b, 92c can also be varied.
  • Producer efficiency as a function of the temperature level is to be illustrated by 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.
  • a condensing boiler As an example.
  • Systems for the heating of air heaters of HVAC systems are usually designed for constant flow temperatures. Given the maximum heating power of an air heater, the length of the component depends on the heating medium flow temperature and the temperature spread. The length of the air heater also determines the air-side pressure drop of the component. Since, in addition to the pressure losses in the sewer system, the sum of the pressure losses of all components of the air handling unit has to be applied by the fan as delivery pressure over the duration of the operating hours, it makes sense to minimize the overall lengths of the heat exchangers in order to reduce the air side pressure losses. Accordingly, the supply temperature level is set correspondingly high for air heaters. Typical design temperatures are between 60 ° and 90 ° C. The adaptation of the temperature level to the load then takes place at the respective air heater by admixing 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 load-dependent lower setpoint temperatures (partial load range). Condensation of the steam produced during the combustion process of fossil fuels increases the efficiency of the boiler, for example in the case of gas by about 10%. For gas boilers with calorific value utilization, this only happens at a temperature level of the combustion gases of less than 60 ° C; for oil boilers, even at temperatures below 50 ° C. Flow temperatures in partial load operation of less than 55 ° C would therefore make energy sense for gas boiler. For certain air conditions, for example when humidifying the air by means of a spray humidifier, air heating may become necessary even in summer.
  • the coolant flow temperature is maintained in the dew point of the air, so could be a significant increase in the cold water inlet temperature.
  • the heat losses of the distribution lines are proportional to the temperature difference between the ambient air and the water.
  • tUm 20 ° C
  • a reduction in the heating water inlet temperature from 80 ° C to 50 ° C would result in a reduction of heat losses of 50%.
  • the heat losses of a cold water network decreased by more than 40% at the same ambient temperature with an increase from 6 ° C to 12 ° C.
  • the proportion of these losses in the total energy consumption depends on the length of the pipelines and their insulation. Since the minimum insulation thicknesses are specified by the legislator, the variable is mainly to be seen in the length of the pipe network.
  • FIG. 14 shows a schematic illustration of the arrangement from FIG. 13 with a control device 110 which couples to the three-way valves 98a, 98b, 98c as well as the heat generators 93, 94 and a flow connection 111 of the hydraulic switch 95.
  • the temperature in the secondary circuit 91 is controlled as a function of the temperatures or the positions of the three-way valves 98a, 98b, 98c in the supply circuits 92a, 92b, 92c.
  • the temperature in the area of the flow distributor is influenced so that the supply circuit with the highest demand is supplied with water of a sufficient temperature level.
  • the temperature level of the flow distributor is selected in the partial load range above the level in the supply chain with the highest demand, for example, the position of the three-way valve for this supplier circle a predetermined manipulated variable, for example 90th %>, may not exceed. If this limit is exceeded, the setpoint of the flow temperature is increased accordingly. If the manipulated variable falls below a likewise predetermined limit value, for example 80%>, the flow temperature is lowered.
  • the temperature in the secondary circuit 91 directly as a function of the temperatures in the supply circuits 92a, 92b, 92c. In cooling, the temperature is in the flow Distributor therefore below the lowest temperature in the supply circuits 92a, 92b, 92c.
  • the manipulated variable of the respective controller (not shown) can be used.
  • the maximum signal determines the change in the setpoint for the follow-up control of the heat generator or the chillers.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Air Conditioning Control Device (AREA)
  • Central Air Conditioning (AREA)

Abstract

L'invention concerne un procédé de conditionnement d'air contrôlé dans une installation de ventilation, procédé selon lequel un état visé de l'air, qui est prédéfini et caractérisé au moins par la température et l'humidité de l'air, est réglé pour de l'air se trouvant dans un état initial, l'air qui se trouve dans cet état initial étant conditionné au moyen d'un refroidisseur d'air (42) pour lequel, lors du conditionnement de l'air, à la fois un débit massique et une température d'entrée d'un fluide de refroidissement amené au refroidisseur d'air (42) sont réglés, le fluide de refroidissement étant amené au refroidisseur d'air (42) via un dispositif de thermorégulation (45), au moyen duquel la température d'entrée du fluide de refroidissement est réglée, et via un dispositif de réglage de débit massique (44), au moyen duquel le débit massique du fluide de refroidissement est réglé, et un dispositif de réglage se couplant au dispositif de réglage de débit massique (44) et au dispositif de thermorégulation (45) et réglant le dispositif de réglage de débit massique (44) et le dispositif de thermorégulation (45) pour régler l'état de l'air en fonction de l'état visé prédéfini. L'invention concerne également un dispositif permettant un conditionnement contrôlé de l'air.
EP12821249.5A 2012-01-13 2012-12-17 Procédé de conditionnement d'air contrôlé dans une installation de climatisation et dispositif Active EP2802822B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE201210100304 DE102012100304A1 (de) 2012-01-13 2012-01-13 Verfahren zur geregelten Luftkonditionierung in einer lufttechnischen Anlage und Vorrichtung
DE102012106819 2012-07-26
DE102012107094 2012-08-02
PCT/DE2012/100383 WO2013104350A2 (fr) 2012-01-13 2012-12-17 Procédé de conditionnement d'air contrôlé dans une installation de ventilation et dispositif

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EP2802822A2 true EP2802822A2 (fr) 2014-11-19
EP2802822B1 EP2802822B1 (fr) 2020-04-08

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DE102013207449A1 (de) * 2013-04-24 2014-10-30 Dürr Systems GmbH Verfahren zum Konditionieren von Luft und Konditionieranlage
CN104633851B (zh) * 2015-01-20 2018-05-01 四川长虹电器股份有限公司 一种信息输出方法及控制设备
CN105371439B (zh) * 2015-11-30 2018-05-18 珠海格力电器股份有限公司 空调器及其风量控制方法和装置
CN115829786B (zh) * 2023-02-16 2023-04-28 国网浙江省电力有限公司金华供电公司 一种基于空调负荷的电网响应调节方法

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DE102009007591B3 (de) * 2009-02-05 2011-03-10 Hochschule für Technik und Wirtschaft Berlin. Verfahren und Vorrichtung zur Luftkonditionierung

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WO2013104350A2 (fr) 2013-07-18
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