EP2394101A1 - Verfahren und vorrichtung zur luftkühlung und luftentfeuchtung - Google Patents
Verfahren und vorrichtung zur luftkühlung und luftentfeuchtungInfo
- Publication number
- EP2394101A1 EP2394101A1 EP10708890A EP10708890A EP2394101A1 EP 2394101 A1 EP2394101 A1 EP 2394101A1 EP 10708890 A EP10708890 A EP 10708890A EP 10708890 A EP10708890 A EP 10708890A EP 2394101 A1 EP2394101 A1 EP 2394101A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- air
- coolant
- mass flow
- circuit
- temperature
- 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.)
- Withdrawn
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
- F24F11/00—Control or safety arrangements
-
- 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
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
-
- 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
- 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
- F24F11/85—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 variable-flow pumps
-
- 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
- F24F3/12—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 treatment of the air otherwise than by heating and cooling
- F24F3/14—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 treatment of the air otherwise than by heating and cooling by humidification; by dehumidification
- F24F2003/144—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 treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only
- F24F2003/1446—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 treatment of the air otherwise than by heating and cooling by humidification; by dehumidification by dehumidification only by condensing
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2221/00—Details or features not otherwise provided for
- F24F2221/56—Cooling being a secondary aspect
Definitions
- the invention relates to a method and a device for air cooling and dehumidification.
- Ventilation systems for workplaces and meeting rooms are often used to maintain not only indoor air quality, but also thermal comfort.
- these systems are usually equipped with system components so that at least three thermodynamic air treatments can be performed: heating, cooling and dehumidifying.
- the installations must be controlled and controlled in such a way that both objectives (maintenance of indoor air quality and thermal comfort) are achieved, although there may well be varying thermal loads and material loads in the room and for persons in the room an external air mass flow necessary for hygienic reasons must be complied with.
- the comfort zone in air-conditioned workplaces is defined in terms of temperature and humidity.
- DIN EN ISO 7730 the operating temperature for the cooling case for category B office premises is given in a range of 24,5 0 C ⁇ 1,5 K.
- the DIN EN 13779 of 2007 proposes for the summer for the moisture loading a range between 6 and 12 g / kg.
- the room air temperature and the relative humidity should be run over the year according to a setpoint program that provides higher values for room air temperature in summer and higher relative humidity values than in winter. This sliding operation takes into account the seasonal cooling and moisture loads.
- thermodynamics of humid air is called psychrometry.
- the air is a gas-vapor mixture in which the component is referred to as vapor, which can condense in the temperature and pressure range under consideration as a liquid or as a solid.
- the other components are added to the component group "Gas”. summarized and remain unchanged for the temperature range considered in their amount.
- moist air can be regarded as a mixture of ideal gases. Since at random temperature not arbitrary amounts of steam mix with the non-condensing gas, three states are distinguished. In the unsaturated state, only the gas phase is present. The partial pressure of the vapor is less than the saturation pressure of the vapor in the mixture. In the saturated state, the partial pressure of the steam is just the saturation pressure of the vapor in the mixture. Gas phase and incipient condensate phase have the same temperature T (thermal equilibrium) and the same total pressure (mechanical equilibrium). In the supersaturated state gas and condensate phase are present. In the gas phase, the relations of the saturated state apply.
- the cooling and dehumidification of the air in central ventilation systems is usually carried out by means of 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.
- hydraulic power control which is usually realized by changing the coolant flow 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).
- 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.
- the air flow to the air cooler must therefore be either heated (dehumidification determines the cooling), or the air flow must be moistened (cooling determines the dehumidification).
- Each of the two known circuits changes the capacity control of the air cooler exactly one size of the coolant flow.
- the mass flow (the quantity) is regulated.
- the coolant flow temperature is controlled according to the performance requirements.
- 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 to obtain the desired air condition.
- the object of the invention is to provide a method and a device for air cooling and dehumidification by means of an air conditioning system, which enables a targeted and energy-efficient adjustment of a target air condition characterized by air humidity and air temperature.
- a method of air cooling and dehumidification by means of an air conditioning system wherein air is controlled with an initial air condition by means of an air cooler and optionally dehumidified to set a predetermined target air condition characterized by humidity and air temperature, by a coolant supply associated with the air cooler for a coolant supplied to the air cooler, both a coolant mass flow and a coolant inlet temperature are regulated in accordance with the outlet air state and the predetermined target air state.
- an apparatus for air cooling and dehumidification comprising: an air cooler configured to cool and optionally dehumidify air having an outlet air condition to set a predetermined target air condition characterized by air humidity and air temperature; and a coolant supply device for a coolant to be supplied to the air cooler, which is configured to regulate both a coolant mass flow and a coolant inlet temperature according to the output air state and the predetermined target air state.
- the proposed techniques are used for air conditioning, in particular room air conditioning.
- Air coolers with conventional hydraulic circuits are only partially able to set desired air conditions in the case of cooling.
- Known quantity-controlled air coolers are e eergetic then inefficient, if the desired cooling capacity leads to an unnecessarily high dehumidification performance.
- mixing-controlled air coolers always waste cooling energy when dehumidification is necessary in addition to the pure cooling capacity.
- these disadvantages are now overcome.
- a precise control of air cooling and - dehumidification is made in thedemittezu slaughterhouse.
- Both the quantity and the inlet temperature of the coolant for the air cooler are included in the coolant supply. guiding device regulated. This allows energy-efficient manner a precise adjustment of a desired Ziel Kunststofftechnikes.
- a preferred development of the invention provides that the regulation of the coolant mass flow and the coolant inlet temperature is carried out with the aid of a hydraulic circuit of the coolant supply device.
- the regulation of the coolant mass flow and the coolant inlet temperature is carried out with the aid of an integrated control circuit comprised of the coolant supply device, in which a mixture-controlled circuit is formed with a delivery-controlled pump device.
- an integrated control circuit is formed, which represents an integration of the mixing-controlled circuit and the quantity-controlled circuit.
- the coolant supplied to the air cooler is determined with respect to the quantity (coolant mass flow) by the delivery-regulated pump and with respect to the temperature by the coolant return admixture.
- An advantageous embodiment of the invention provides that the regulation of the coolant mass flow and the coolant inlet temperature is carried out with the aid of a series connection of a mixture-controlled and a quantity-controlled circuit encompassed by the coolant supply device. It can be provided that the coolant supply device consists only of the mixing-controlled and the quantity-controlled circuit.
- the regulation of the coolant mass flow and the coolant inlet temperature is carried out with the aid of an integrated control circuit comprising the coolant supply device, in which a pump device with constant delivery pressure and a valve control device are formed.
- An embodiment of the invention provides that the regulation of the coolant mass flow and the coolant inlet temperature is carried out with the aid of an integrated control circuit comprised of the coolant supply device, in which a pump device with constant rotational speed and a bypass device are formed.
- the bypass device preferably comprises a regulated bypass. Description of preferred embodiments of the invention
- Fig. 2 is a schematic representation of the known change in state of humid air in
- FIG. 3 is a schematic representation of a device for air cooling and dehumidification with an integrated hydraulic circuit consisting of a derischgeregelten circuit with a direct flow rate controlled pumping device,
- FIG. 4 is a schematic representation of a device for air cooling and dehumidification with an integrated hydraulic circuit consisting of a derischge- regulated circuit with an indirectly flow rate controlled pumping device,
- FIG. 5 is a schematic representation of a device for air cooling and dehumidification with an integrated hydraulic circuit consisting of a derischgeregelten circuit with an unregulated pumping device with controlled bypass,
- FIG. 6 is a schematic representation of a device for air cooling and dehumidification with an integrated hydraulic circuit consisting of a series circuit of derischgeregelter circuit with unregulated pumping device and a volume-controlled circuit,
- FIG. 7 shows symbols for elements of the analagenic scheme in FIGS. 3 to 6 and FIG. 8, FIG.
- FIG. 8 is a simplified system diagram of an air-only system with heat recovery and recirculation path, wherein a humidification using a steam humidifier,
- FIGS. 3 to 6 shows a schematic representation of a control strategy for the devices for air cooling and dehumidification in FIGS. 3 to 6 in the simplified Mollier diagram;
- FIG. 10 is a simplified control diagram for the hydraulic circuit according to FIG. 3;
- FIG. 11 is another simplified control diagram for the hydraulic circuit according to FIG. 3;
- FIG. 13 is another simplified control diagram for the hydraulic circuit of FIG. 3, and 14 shows a further simplified control diagram for the hydraulic circuit according to FIG. 3.
- FIG. 3 shows a schematic representation of a device for air conditioning (cooling and dehumidification) with an integrated control circuit, in which a delivery-controlled pumping device is integrated into a delivery-controlled circuit.
- the integrated circuit is executed in the illustrated embodiment as a hydraulic circuit, which can also be referred to as "Optimized Dehumidification Control Loop" (OpDeCoLo), they the targeted adjustment of a characterized by humidity and air temperature Ziel KunststoffSches using a liquid-cooled air cooler with the least possible energy use (cooling and conveying energy) allows.
- OFCoLo Optimized Dehumidification Control Loop
- a coolant supply device 11 is coupled to an air cooler 10, which is formed with a mixing valve 12 and a speed-controlled pump 13.
- the mixing valve 12 connects a chilled water supply 14 provided by a refrigerator (not shown) with the admixture of a coolant return 15 for the coolant supply 16 to be fed into the air cooler 10 with the desired temperature and quantity.
- the state of the air emerging from the air cooler 10 becomes detected by a temperature measuring device 17 and a humidity measuring device 18.
- the circuit in Fig. 3 corresponds to the derischgeregelten circuit, but in which instead of a pump with a constant flow rate, the variable-speed pump 13 is installed.
- the mixing valve 12, which defines three ways, is provided with an actuator 19.
- the speed control of the variable-speed pump 13 can be done by means of a frequency converter (not shown).
- a frequency converter not shown.
- the air cooler 10 and the coolant mass flow are designed so that the cooling capacity is provided with a coolant inlet temperature above the respective dew point of the moist air. In many cases, this requires a larger-sized air cooler than in the case of a volume-controlled hydraulic circuit or a derischgeregelten circuit with humid cooling.
- a pump 40 with constant delivery pressure together and a controlled passage valve 41 (see Fig. 4) or a pump 50 with constant speed with a bypass 51 (see Fig. 5) may be provided, which is preferably carried out regulated.
- the dehumidification of the air is determined by selecting the cooling water inlet temperature, the cooling capacity, however, by means of the coolant mass flow. The respective total cooling power from cooling and dehumidification of the air cooler 10 thus results as a combination of coolant mass flow and coolant inlet temperature.
- FIG. 6 shows a schematic representation of an apparatus for air conditioning (cooling and dehumidification) with an integrated control circuit consisting of a series circuit of derischgeregelter circuit 60 with non-flow rate controlled pumping device 61 and a quantity-controlled circuit 62.
- a series circuit of derischgeregelter circuit 60 with non-flow rate controlled pumping device 61 and a quantity-controlled circuit 62.
- the volume-controlled air cooler is much more efficient in the case of desired dehumidification than the mixed-air cooler.
- the savings potential for the device for air conditioning according to FIGS. 3 to 6 compared with the known volume-controlled air cooler is obtained in particular for the following cases:
- An air-only system with regenerative heat recovery (WRG) and a recirculation damper control corresponds to the state of the art for ventilation systems that have to dissipate high thermal loads with changing occupancy.
- WRG regenerative heat recovery
- a recirculation system was selected for heat recovery, which can be easily bridged if necessary by switching off the pump and, in addition, offers the possibility of being able to conduct outside air and exhaust air flow in separate locations. Existing plants are often retrofitted with such systems.
- Table 1 Boundary conditions for determining the energy requirement for air cooling as a function of the hydraulic circuit of the air cooler
- the ventilation system should be operated in such a way that the heat recovery system is only active for the summer, when the temperature of the outside air (ODA) exceeds that of the exhaust air (EHA).
- ODA outside air
- EHA exhaust air
- PODA pretreated outside air
- RCA mixing chamber only recirculated air
- PODA pretreated outside air flow
- the moisture content of the circulating air was assumed to be 1 g / kg higher than that of the outside air due to humidity sources in the room.
- the boundary conditions of the comparison are shown in Table 1.
- the recirculating air admixture not only reduces the temperature reduction to be provided by the air cooler, but also reduces the difference between the moisture content of the outside air and the set point after the air cooler.
- the device for air conditioning according to FIG. 3 produces a combination of both types of circuit, wherein in the boundary region there is either a mixture-controlled or a quantity-controlled cooler.
- Fig. 7 shows symbols for elements of the plant scheme in Figs. 3 to 6 and Fig. 8.
- an air-only system with heat recovery and recirculation path is shown in simplified, wherein a humidification by means of a steam humidifier.
- FIG. 8 shows a complete air-only installation, only the cooling energy requirement (air cooling and dehumidification) is included in the estimation of the energy-saving potential. Neither Reheating or humidification are considered in this comparison. Also not included were the energy costs for operating the pumps. Again, the hydraulic circuit shown in Fig. 3 cuts off better than the two base circuits and the circuits of Figs. 4 to 6.
- Table 2 Specific annual cooling energy requirement for a mass air flow of 1 kg / h for climatic data for Mannheim
- a speed-controlled pump is used on the hardware side in one of the embodiments described above.
- the concept of an associated control technology that not only the coolant mass flow or the coolant inlet temperature, but also the respective optimum of coolant inlet temperature and coolant telematic power is shown below.
- the speed control of the pump can be carried out either by means of a frequency converter (see FIG. 3) or, as shown in FIG. 4, by means of a change in the flow resistance with the aid of a valve.
- the hydraulic circuits of Fig. 5 and Fig. 6 with unregulated pumping devices are also able to achieve the cooling energy savings according to Table 2, but are characterized by higher delivery costs.
- the surface temperature of the cooler When cooling without dehumidification, the surface temperature of the cooler must never be equal to or lower than the dew point temperature of the moist air to be cooled. Therefore, in this case, the flow temperature of the cooling fluid for the air cooler must not fall below the dew point temperature of the moist air. Since the cooling capacity depends on the average surface temperature of the air cooler, the air can not be cooled down to the saturation line. Therefore, in this case, the air cooler is operated at a high pump speed, the power adjustment being done by changing the refrigerant return admixture.
- the water vapor loading of the air is regulated.
- both the pump speed and the coolant return admixture are changed so that the target point of the air is achieved at the radiator outlet.
- the flow rate (pump speed), the flow rate control and the coolant inlet temperature (coolant return admixture) takes over the admixing.
- the delivery mass flow at constant coolant temperature determines the slope of the state change in the Mollier diagram; At constant flow, the coolant inlet temperature determines the sensible cooling capacity.
- the two parameters are not independent of each other because the effective surface temperature also changes due to the influence on the coolant return temperature as the coolant inlet temperature and the mass flow rate changes both has an influence on the sensitive cooling performance and the dehumidification of the airflow.
- the effective surface temperature also changes due to the influence on the coolant return temperature as the coolant inlet temperature and the mass flow rate changes both has an influence on the sensitive cooling performance and the dehumidification of the airflow.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fuzzy Systems (AREA)
- Mathematical Physics (AREA)
- Signal Processing (AREA)
- Central Air Conditioning (AREA)
- Air Conditioning Control Device (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009007591A DE102009007591B3 (de) | 2009-02-05 | 2009-02-05 | Verfahren und Vorrichtung zur Luftkonditionierung |
PCT/DE2010/000131 WO2010088893A1 (de) | 2009-02-05 | 2010-02-05 | Verfahren und vorrichtung zur luftkühlung und luftentfeuchtung |
Publications (1)
Publication Number | Publication Date |
---|---|
EP2394101A1 true EP2394101A1 (de) | 2011-12-14 |
Family
ID=42140103
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10708890A Withdrawn EP2394101A1 (de) | 2009-02-05 | 2010-02-05 | Verfahren und vorrichtung zur luftkühlung und luftentfeuchtung |
Country Status (4)
Country | Link |
---|---|
US (1) | US20120048954A1 (de) |
EP (1) | EP2394101A1 (de) |
DE (1) | DE102009007591B3 (de) |
WO (1) | WO2010088893A1 (de) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2013019537A2 (en) * | 2011-07-29 | 2013-02-07 | Carrier Corporation | Hvac systems |
EP2802822B1 (de) * | 2012-01-13 | 2020-04-08 | Hochschule für Technik und Wirtschaft Berlin | Verfahren zur geregelten luftkonditionierung in einer lufttechnischen anlage und vorrichtung |
DE102012100304A1 (de) | 2012-01-13 | 2013-07-18 | Hochschule Für Technik Und Wirtschaft Berlin | Verfahren zur geregelten Luftkonditionierung in einer lufttechnischen Anlage und Vorrichtung |
DE102012018627A1 (de) | 2012-09-21 | 2014-03-27 | Ullrich Taut | Verfahren und Vorrichtung zum Betreiben eines Luftkühlers in einer lüftungstechnischen Anlage |
EP2936952B1 (de) * | 2012-12-18 | 2018-12-05 | Schneider Electric IT Corporation | Kühleinheit und verfahren |
JP6951085B2 (ja) * | 2017-02-24 | 2021-10-20 | 株式会社竹中工務店 | 空調システム |
JP7002918B2 (ja) * | 2017-11-08 | 2022-02-04 | 三菱電機株式会社 | 換気システム、空調システム、換気方法及びプログラム |
DE102019117378A1 (de) * | 2019-06-27 | 2020-12-31 | Rheinisch-Westfälische Technische Hochschule (RWTH) Aachen, Körperschaft des öffentlichen Rechts | Verfahren und System zu Regelung eines Medienparameters des Mediums auf der Sekundärseite eines Wärmeübertragers |
DE102020115301B3 (de) * | 2020-06-09 | 2021-05-06 | EnBW Energie Baden-Württemberg AG | Gasdruckregelanlage, Entfeuchtungseinrichtung für eine Gasdruckregelanlage und Verfahren zum Betreiben einer Gasdruckregelanlage |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
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DE2116857B2 (de) * | 1971-04-06 | 1974-02-07 | Gesellschaft Fuer Kernforschung Mbh, 7500 Karlsruhe | Verfahren zum Kühlen und Entfeuchten von Luft |
NZ210198A (en) * | 1983-11-18 | 1987-01-23 | Teledyne Ind | Cooling cabins of parked aircraft using system located external to the aircraft |
DE3610069A1 (de) * | 1986-03-25 | 1987-10-01 | Siemens Ag | Anordnung zum regeln von temperatur und feuchte |
DE4431041C2 (de) * | 1994-09-01 | 1996-09-19 | Himmelsbach Johann | Verfahren und Vorrichtung zur selbstadaptiven Steuerung einer Kraftfahrzeugheizung |
DE19849662A1 (de) * | 1998-10-29 | 2000-05-04 | Burkhard Heyden | Verfahren zur Beeinflussung der Raumtemperatur und Raumluftfeuchte un thermo-hygro-aktives Bauelement hierzu |
DE102005012926B4 (de) * | 2005-03-21 | 2007-02-01 | Deutsches Zentrum für Luft- und Raumfahrt e.V. | Einrichtung zur Erweiterung von Einsatzmöglichkeiten eines zu Forschungszwecken entsprechend umgerüsteten Fahrzeugs |
PL1710516T3 (pl) * | 2005-03-29 | 2009-04-30 | Moeritz Martin | Urządzenie i sposób nawilżania strumienia powietrza |
CN100587346C (zh) * | 2005-07-28 | 2010-02-03 | 克里纳加热与冷却设备公司 | 包括毛细管垫的空气冷却与空气除湿模块及其使用方法 |
JP2007285579A (ja) * | 2006-04-14 | 2007-11-01 | Toshiba Corp | 空調制御装置 |
US20080310112A1 (en) * | 2007-06-13 | 2008-12-18 | Johnson Controls Technology Company | System and Method for Providing Dewpoint Control in an Electrical Enclosure |
-
2009
- 2009-02-05 DE DE102009007591A patent/DE102009007591B3/de not_active Expired - Fee Related
-
2010
- 2010-02-05 WO PCT/DE2010/000131 patent/WO2010088893A1/de active Application Filing
- 2010-02-05 EP EP10708890A patent/EP2394101A1/de not_active Withdrawn
- 2010-02-05 US US13/147,396 patent/US20120048954A1/en not_active Abandoned
Non-Patent Citations (2)
Title |
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None * |
See also references of WO2010088893A1 * |
Also Published As
Publication number | Publication date |
---|---|
US20120048954A1 (en) | 2012-03-01 |
WO2010088893A1 (de) | 2010-08-12 |
DE102009007591B3 (de) | 2011-03-10 |
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