EP2326836A2 - Procédé et dispositif de gestion de l'air dans des installations d'énergie éolienne - Google Patents

Procédé et dispositif de gestion de l'air dans des installations d'énergie éolienne

Info

Publication number
EP2326836A2
EP2326836A2 EP09781552A EP09781552A EP2326836A2 EP 2326836 A2 EP2326836 A2 EP 2326836A2 EP 09781552 A EP09781552 A EP 09781552A EP 09781552 A EP09781552 A EP 09781552A EP 2326836 A2 EP2326836 A2 EP 2326836A2
Authority
EP
European Patent Office
Prior art keywords
air
tower
outside air
flow
supply
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Withdrawn
Application number
EP09781552A
Other languages
German (de)
English (en)
Inventor
Frank Buss
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.)
Individual
Original Assignee
Individual
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
Application filed by Individual filed Critical Individual
Publication of EP2326836A2 publication Critical patent/EP2326836A2/fr
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D9/00—Adaptations of wind motors for special use; Combinations of wind motors with apparatus driven thereby; Wind motors specially adapted for installation in particular locations
    • F03D9/20—Wind motors characterised by the driven apparatus
    • F03D9/25—Wind motors characterised by the driven apparatus the apparatus being an electrical generator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03G—SPRING, WEIGHT, INERTIA OR LIKE MOTORS; MECHANICAL-POWER PRODUCING DEVICES OR MECHANISMS, NOT OTHERWISE PROVIDED FOR OR USING ENERGY SOURCES NOT OTHERWISE PROVIDED FOR
    • F03G6/00—Devices for producing mechanical power from solar energy
    • F03G6/02—Devices for producing mechanical power from solar energy using a single state working fluid
    • F03G6/04—Devices for producing mechanical power from solar energy using a single state working fluid gaseous
    • F03G6/045—Devices for producing mechanical power from solar energy using a single state working fluid gaseous by producing an updraft of heated gas or a downdraft of cooled gas, e.g. air driving an engine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D13/00—Assembly, mounting or commissioning of wind motors; Arrangements specially adapted for transporting wind motor components
    • F03D13/20—Arrangements for mounting or supporting wind motors; Masts or towers for wind motors
    • F03D13/25—Arrangements for mounting or supporting wind motors; Masts or towers for wind motors specially adapted for offshore installation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03D—WIND MOTORS
    • F03D80/00—Details, components or accessories not provided for in groups F03D1/00 - F03D17/00
    • F03D80/60—Cooling or heating of wind motors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/58—Cooling; Heating; Diminishing heat transfer
    • F04D29/582—Cooling; Heating; Diminishing heat transfer specially adapted for elastic fluid 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
    • 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
    • F24F3/153—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 with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/20—Heat transfer, e.g. cooling
    • F05B2260/24—Heat transfer, e.g. cooling for draft enhancement in chimneys, using solar or other heat sources
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2260/00—Function
    • F05B2260/60—Fluid transfer
    • F05B2260/64—Aeration, ventilation, dehumidification or moisture removal of closed spaces
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/54—Free-cooling systems
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/40—Solar thermal energy, e.g. solar towers
    • Y02E10/46—Conversion of thermal power into mechanical power, e.g. Rankine, Stirling or solar thermal engines
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/727—Offshore wind turbines

Definitions

  • the invention relates to a method and a device for air treatment in wind power plants, in particular in offshore wind power plants, according to the preamble of claims 1 and 28 to 30.
  • Wind turbines or correct wind energy systems and in particular offshore wind energy systems consist according to the schematic diagram in Fig. 1 from a grounded in the seabed tower 10, at the top of a nacelle 11 is arranged, in which a generator is located, via a drive shaft and a Gear is connected to three rotor blades 12 in the illustrated example, the angle of attack are generally adjustable to optimize the wind drive.
  • the electrical power output by the generator is processed by means of electrical and electronic components and units 16 such as switchgear, switching devices, control and regulating devices, transformers, frequency converters, etc., and transmitted via cables to the mainland.
  • the arranged in an aggregate module 15 of the tower 10 electrical and electronic units 16 control and also regulate the operation of the generator, the position of the rotor blades etc.
  • the heat-dissipating electrical and electronic units 16 is outside air AL via a generally below the unit module 15 arranged air inlet opening 14, for example, an opening in an access door in the tower 10, of an air treatment unit 2, the components are shown schematically in Fig. 2 and be described below, sucked, cleaned and discharged with positive pressure as supply air ZL to the interior of the tower 10 so that the introduced and largely purified supply air flow ZL flows through the aggregate module 15, the heat absorbed by the electrical and electronic components and aggregates 16 radiation and discharged via outlet openings 13 in the nacelle 1 1 as exhaust air FL to the environment.
  • Fig. 2 shows a schematic representation of a conventional air treatment device 2 for desalination of the sea air and for generating an overpressure in the interior of the tower 10.
  • the air treatment device 2 a first droplet 21 as a main separator for coarse pre-separation of rain, spray, etc.
  • coalescence separators 22, 23 designed as aerosol filters are provided, which bind aerosols and form larger droplets.
  • a second droplet separator 24 follows as a post-separator, which intercepts and separates the previously formed droplets.
  • the required air flow is generated by means of an outside air or overpressure fan 25.
  • the air conditioning system according to FIG. 2 provided in the offshore wind power plant 1 thus fulfills the following tasks:
  • the introduced sea air (outside air) is cleaned by the salt aerosols contained in the air to protect against the corrosion within the tower 10 of the offshore wind energy plant 1 in the unit module 15 arranged electrical and electronic units 16;
  • the supply and overpressure fan 45 is operated as a function of the external wind speed pressure-dependent, with an overpressure of about 2000 Pa can be generated, so that even in strong winds, i. at wind speeds up to 56 m / sec, the introduced, mostly purified
  • Zu Kunststoff ZL essentially escape in the gondola 11 existing leaks 3 and escape through corresponding overpressure flaps, ie can flow to the outside, while the ingress of unpurified, salty sea air even in strong winds in the interior of the tower 10 and the nacelle 1 1 by the generated pressure is prevented.
  • a disadvantage of this conventional air treatment in offshore wind energy systems 1 is that the treatment of the sea or outdoor air AL achieved by desalination, a strong reduction of the salt content, but a residual content of salt is permanently entered into the tower 10, in particular in the form of The aerosol dissolved in the outside air, which can not be filtered out by the droplet and Koaleszenzabscheidern the air treatment unit 2. 0.005 mg / m 3 is exceeded 100 times, so that the electrical and electronic units 16 are contaminated despite the air conditioning and after a relatively short time considerable corrosion of the electrical and electronic Aggre gate 16 takes place.
  • Salt has different states of aggregation depending on the moisture content.
  • salt is in the liquid state of aggregation.
  • a moisture content between approx. 40% and approx. 70% a mixed form of liquid salt, salt aerosols and salt particles is present, while with a moisture content of ⁇ approx. 40% salt is present in bound particles (as it were as dust). Since salt crystallizes to particles at a moisture value of less than approx. 40%, a reduction or elimination of the salt content by means of a high-performance filter is possible if a moisture content of less than approx. 40% is achieved in each season.
  • the present invention has for its object to provide a method and an apparatus for air treatment in wind power plants and in particular in offshore wind energy systems, the elimination or reduction of the salt and moisture content and thus the risk of condensation (dew point below) of ensure the unit module and air discharged into the tower or nacelle with positive pressure.
  • the solutions according to the invention ensure elimination or at least a considerable reduction of the salt and moisture content and thus reduction of the risk of condensation due to dew point undershooting of an outside or supply air supplied to the unit module and into the tower or the nacelle by an outside air fan with overpressure. Volume flow and thus the risk of corrosion in the Aggregate module arranged electrical and electronic units and the inner wall and the devices in the tower and in the nacelle.
  • This simple air treatment device assumes that by heating the outside air to a relative humidity of 40%, the salt aerosols crystallized to particles can be separated in a high-performance filter as salt particles. Although this is a significant reduction of the residual salt content and thus the risk of corrosion in the unit module and inside the tower and connected in the nacelle, but can not be ensured under all climatic conditions and year-round, that the air flow in the aggregate module and inside the tower and the nacelle is maintained in such a way that, on the one hand, the heat emitted by the electrical and electronic units heat is dissipated with sufficient certainty and on the other hand, a risk of corrosion inside the tower and the nacelle can be excluded.
  • the wind energy plant is not in operation for many years of the year, for example in storms, light winds, incidents and for maintenance purposes.
  • an emergency operation is required which is insufficiently ensured with this method can be.
  • a comparison with the prior art substantially improved air treatment system is therefore characterized in that the cooled via the air inlet opening from the environment of the tower sucked wet and salty outside air cooled in an air treatment device and thereby the absolute humidity of the outside air is lowered, that the cooled and dehumidified outside air heats is reached to a predetermined relative humidity of the outside air, in which the Saiz aerosols contained in the outside air are at least partially crystallized, that the crystallized salt aerosols and salt particles contained in the outside air are separated and that the dehumidified and desalinated outside air as supply air to the interior of the tower and / or delivered to the aggregate module.
  • the moist and saline outside air drawn in via the air inlet opening from the surroundings of the tower is heated until a predetermined relative humidity of the outside air is achieved, at which the salt aerosols contained in the outside air are at least partially crystallized, the crystallized salt aerosols and salt particles contained in the outside air are separated and the dehumidified and desalinated outside air is indirectly, freely cooled and discharged as cooled supply air to the interior of the tower and / or to the aggregate module.
  • the indirectly, freely cooled supply air before delivery to the interior of the tower and / or to the unit module) can be further cooled down with a mechanical cooling device.
  • the air can absorb up to 27 g / kg of water along the line A, while at a temperature of -13 0 C, the air corresponding to the line B absorbs only 1 g / kg. This behavior expresses the strength of the electrolyte.
  • Fig. 6 shows the range of critical humidity, i. H. the range of 70 to 100% relative humidity in the Mollier-h, x-diagram.
  • the temperature and humidity values of the locations concerned are entered as a so-called “weather bubble” in relation to the "critical humidity” area shown in FIG. From these representations in the Mollier-h, x diagram, a large number of annual hours are in the range of "critical humidity.” In some areas, the local weather data is almost without exception in the "critical humidity" range.
  • the electrolyte is extremely intensified by the high salt content in the air, for example, when the wind energy plant is located in the coastal area or "offshore.” For this reason, the corrosion rate under the influence of the sea climate is significantly higher than in the interior
  • the weather bubble of the island of Heligoland which is shown in outline in Fig. 6, shows that 8,533 hours per year in the range of "critical humidity", ie in the range of 70-100% relative humidity.
  • Temperature and humidity changes are not only due to the weather, but also in the mechanical cooling of air by means of a condenser, evaporator and
  • a further optimized air treatment system is characterized in that the moist and saline outside air drawn in via the air inlet opening from the environment of the tower is supplied to the cooled and dehumidified outside air to an air treatment device having separate flow paths in which a heat exchanging connection with the outside air is established Circulating air flow is guided in a closed circuit through the unit module and the thermal energy absorbed by the heat dissipation of the electrical and electronic units emits heat to the outside air, is discharged from the under exclusion of the aggregate module heated supply air with pressure to the interior of the tower and the nacelle.
  • the optimized air treatment system ensures efficient heat dissipation of the surface heat emission of the electrical and electronic units and a controlled temperature maintenance in the tower to the nacelle by controlled heat transfer with feed from the waste heat of the electrical and electronic units.
  • the outside air which is still contaminated with salt, no longer flows freely through the aggregate module and thus can not contaminate the electrical and electronic units.
  • the volume flow of the outside air and / or the circulating air are generated independently of each other and controlled and adjusted for adjusting the heat transfer in the unit module and / or the temperature or humidity of the supply air.
  • the control and regulation of the recirculated circulating air allows a stepless adjustment of the required circulating air and thus a circulation of suitable air quantities.
  • variable amounts of air both the outside air to the supply air and the recirculation depending on parameters such as outdoor air temperature, humidity and salt content of the outside air and depending on the required cooling power in the unit module and emergency heating at standstill of the wind energy plant, the air treatment can be significantly influenced.
  • variable air volumes of the outside air supply air or the circulating air is a significant factor on the energy consumption or energy costs given as a reduction in outdoor air supply air and recirculated air quantities in the lowered operation under appropriate weather conditions and lower heat loads in Aggregate module also saves energy costs.
  • the air treatment device includes an air treatment unit with heat recovery, through which the hermetically separated flow paths of the outside air supply air flow and the circulating air flow are guided and arranged in the flow direction of the outside air supply air before and / or after the air treatment unit with heat recovery capacitor or reheat register a dehumidification heat pump containing an evaporator, the at least one condenser or reheat register, and a compressor.
  • the moisture reduction is met in the same way.
  • the arrangement of the condenser of the dehumidification heat pump upstream of the air treatment unit with heat recovery with immediate reheating after cooling in the evaporator of the dehumidification heat pump reduces the cooling effect of the circulating air flow in the air treatment unit with heat recovery, since the outside air supply air was already heated in the condenser , which would be technically disadvantageous, but would not affect the functioning of the dehumidification heat pump.
  • outside air supply air stream is additionally heated immediately after leaving the air treatment unit with heat recovery, ie after the heat released from the circulating air flow, with the energy from the dehumidification process via the condenser or the heat register, then an even more favorable, namely causes lower value of the relative humidity of the outside air supply air.
  • the arrangement of the evaporator and condenser is not necessarily required at the air inlet or air outlet of the plate heat exchanger, but can also be provided somewhere within the channel system of the blown into the tower supply air.
  • the dehumidification heat pump contains two capacitors or reheat registers, of which a first capacitor in the flow direction of the outside air supply air flow in front of the air treatment unit with heat recovery and the second capacitor is arranged in the flow direction of the outside air supply air after the air treatment unit with heat recovery.
  • the arrangement of two capacitors and their mutual circuit has the advantage that the different requirements between summer and winter operation can be better met, since the efficiency of the air treatment unit with heat recovery or its heat transfer is determined by the temperature difference.
  • the first capacitor is preferably used in winter and the second capacitor preferably in summer.
  • both capacitors can be operated in partial load operation, whereby both capacitors are automatically controlled in mutual operation or with variable partial loads.
  • the proportion of the outside air supply air flow guided by the air treatment unit with heat recovery is preferably set as a function of a temperature and / or humidity control of the optimized air treatment system.
  • a condenser is arranged in the circulating-air flow path, to which the heater module in the unit module is switched.
  • condenser or reheat register and compressor when the heating demand in the unit module, for example, in the winter months at low or too low temperatures and / or emergency operation at standstill of the offshore wind energy plant, from the dehumidifying heat pump formed from the evaporator or cooler, condenser or reheat register and compressor be switched in the outside air supply air from the condenser of the dehumidification heat pump to the condenser in the circulating air flow, so that the dehumidification heat pump in the outside air supply air flow AL / ZL heated to the power module module supply air circulating air of the second flow path.
  • the energy for this heating operation is supplied by other offshore wind power plants operated in the network.
  • the supply air flow discharged from the air treatment device to the inside of the tower is guided via a heat exchange device which releases heat energy absorbed from the waste heat of the electrical and electronic units to the supply air flow as a function of the air temperature in the interior of the tower and the nacelle, the supply air at least in the section between the air treatment device and the entrance into the interior of the tower is guided in a supply air duct.
  • the effect and positive consequences of the heat exchange device are that in order to avoid condensation within the tower and the nacelle, the air is heated so far through the heat exchange device, ie an increase in temperature is caused even by the cooling effect of the tower walls and a drop in temperature Supply air in the tower and the nacelle dew point is not reached.
  • the air treatment device not only causes dehumidification and desalination of the outside air discharged from the air treatment device, but also takes over the dehumidification of the unit module by a targeted air extraction from the individual floors or platforms of the unit module via circulating air exhaust air ducts and a targeted air supply via circulating air supply air ducts in the individual floors or platforms of the aggregate module.
  • the supply air discharged by the air treatment device is additionally dehumidified, heated with the energy obtained from the dehumidification process prior to delivery to the interior of the tower and injected into the interior of the tower at high speed and preferably in the center of the tower diameter.
  • the moist and saline outside air drawn in via the air inlet opening from the environment of the tower can be conducted via a mist eliminator for coarse pre-separation of rain, spray.
  • the air treatment system according to the invention is downstream of an air treatment device for desalination of the outside air and for generating an overpressure in the interior of the tower, preferably a first droplet separator for coarse pre-separation of rain, spray and the like, a Koaleszenzabscheider to form larger droplets, a second droplet Having as Nachabscheider for intercepting and separating the previously formed droplets and the required air flow generating outside air or overpressure fan.
  • an air treatment device for desalination of the outside air and for generating an overpressure in the interior of the tower preferably a first droplet separator for coarse pre-separation of rain, spray and the like, a Koaleszenzabscheider to form larger droplets, a second droplet Having as Nachabscheider for intercepting and separating the previously formed droplets and the required air flow generating outside air or overpressure fan.
  • the processed supply air is injected at a high speed obliquely upward, sharp on the tower wall upwards in the tower according to another process feature so that the injected air flow is moved along the tower wall and in the tower creates a rotational movement (vortex flow), which tears air layers and air layers.
  • the above-described methods provide a heat pump with dehumidifying and desalination properties in which the dehumidified and desalinated air, even with total recooling to the outside air level, for example through the tower walls or through mechanical means for free indirect cooling, such as a plate heat exchanger operated with fresh air Dew point can not be reached again and can maintain and guarantee a maximum relative humidity of less than 60% relative humidity through targeted dehumidification, so that a linear increase in corrosion is excluded and the risk of corrosion is permanently significantly reduced.
  • a first device for air treatment in wind power plants, especially in offshore wind energy plants, with a tower at the top of a gondola with a generator and at least one rotor blade and in the interior heat-dissipating electrical and electronic units such as switchgear, switching devices, transformers , Frequency converter and the like are arranged in an aggregate module of the tower and having at least one air inlet opening and an air outlet opening, is sucked through the air inlet opening from the environment of the tower moist and salty outside air, characterized by an air treatment device with a heater or an air heater for heating the outside air or in an air treatment or desalination unit desalinated and dehumidified outside air and a high-performance filter for filtering the particle-salted salt aerosols in the outside air or desalted and dehumidified outside air and the supply of heated supply air through the aggregate module in the tower and in the nacelle.
  • an air treatment device with a heater or an air heater for heating the outside air or in an air treatment or
  • This simple air treatment device makes it possible to deposit the particle-crystallized salt aerosols in a high-performance filter as salt particles by heating the outside air to a relative humidity of 40%.
  • the associated significant reduction of the residual salt content and thus the risk of corrosion in the unit module and in the interior of the tower and in the nacelle can not ensure under all climatic conditions and throughout the year that the air flow in the aggregate module and in the interior of the tower and the nacelle in the Is maintained, so that on the one hand the heat dissipated by the electric and electronic units is dissipated sufficiently safe and on the other hand, a risk of corrosion inside the tower and the nacelle can be excluded.
  • emergency operation possible in the event of storm, light wind, accidents and maintenance.
  • An improved device for air treatment in wind power plants especially in offshore wind energy plants, with a tower at the top of a gondola with a generator and at least one rotor blade and in the interior heat-dissipating electrical and electronic units such as switchgear, switching devices, transformers , Frequency converter and the like are arranged in an aggregate module of the tower and having at least one air inlet opening and an air outlet opening, is sucked through the air inlet opening from the environment of the tower moist and salty outside air, is characterized by an air treatment device with one of an evaporator for Reduction of the absolute moisture content of the supplied outside air or the outside air desalinated and dehumidified in an upstream air treatment or desalination unit, a condenser or a reheat coil for reheating the outside air a uf a relative humidity of 40% or less and a compressor dehumidifying heat pump, and with a high performance filter for salt separation.
  • an air treatment device with one of an evaporator for
  • the improved air treatment device is achieved by cooling the humid and salty outside air while reducing the absolute moisture content of the outside air and the subsequent reheating a moisture level of the treated outside air of less than or equal to 40% relative humidity, so that the salzaerosols still contained in the outside air crystallized and can be deposited in a high performance filter.
  • the supply air flows freely and without special air supply systems into or through the aggregate module and through the upper part of the tower to the nacelle.
  • An optimized air treatment system with a third, optimal device for air treatment in wind power plants, in particular in offshore wind power plants, with a tower, at the upper end of a nacelle with a generator and at least one rotor blade and in the interior heat-releasing electrical and electronic units such as switchgear, switching devices, transformers, frequency converters and the like are arranged in an aggregate module of the tower and having at least one air inlet opening and an air outlet opening, wherein via the air inlet opening from the environment of the tower moist and salty outside air is sucked in, is characterized by an air treatment device with an air treatment device with recuperative heat recovery system and hermetically separated first and second flow paths, wherein the first flow path sucked through the air inlet opening outside air to d it leads to the interior of the tower with the exception of the aggregate module delivered supply air and the second flow path in recirculation mode supply air to the unit module and sucks exhaust air or return air from the unit module.
  • the air treatment device with recuperative heat recovery system includes a plate heat exchanger, which is arranged in the flow direction of the first flow path to a connected to the air inlet opening air treatment device for desalination of the sucked outside air.
  • the optimized air treatment system ensures a powerful cooling of the surface heat dissipation of the electric and electronic units, a controlled temperature maintenance in the tower to the nacelle by controlled heat transfer with power from the waste heat of the electric and electronic units and hermetically separate two air streams that always outside air contaminated with salt no longer flows freely through the aggregate module and thus can not contaminate the electrical and electronic units.
  • the plate heat exchanger on the inlet side of the cooled down in the evaporator of the dehumidification heat pump outside air adjustable bypass flaps with which the number of plates of the plate heat exchanger can be set, which are used in the outside air supply air flow for energy exchange or to be passed to the energy exchange, so that on the adjustment the bypass valves influence the energy exchange and thus the temperature and / or humidity behavior of the air treatment device can be taken and the bypass valves can be included in a temperature and humidity control of the optimized air treatment system.
  • the outside air fan is arranged on the suction side, in the flow direction of the outside air to the supply air behind the air treatment device.
  • the outside air fan can be arranged both on the suction side and on the pressure side.
  • the latter for example, when the outside air fan is already part of an existing, conventional air handling unit and the air treatment device is retrofitted.
  • the arrangement of the outside air fan on the suction side of the air treatment unit as it is located in dry, salt-free air, which considerably reduces the risk of corrosion of the outside air fan and therefore requires only a low level of material quality from the outside air fan.
  • the arrangement of the outside air fan on the suction side allows placement of the Conceptluftventila- sector, which are possible and suitable from the unit module on all intermediate decks of the tower to the nacelle as a site.
  • the desalted and dehumidified supply air in the supply air duct is guided in a consistent continuation of the separation of the two flow paths through the plate heat exchanger, from the circulating air circulating in the unit module to the inside of the tower Moisture or salt aerosols still contained in the supply air can not reach the sensitive electrical and electronic devices in the aggregate module.
  • the supply air is treated in such a way that the dehumidified and desalinated supply air delivered to the interior of the tower and / or the aggregate module does not reach the dew point again, even if it cools down to the value of the outside air, and a maximum relative humidity value through targeted dehumidification performance
  • the electric and electronic units arranged in the tower and the nacelle of the wind power plant are sufficiently cooled for safe, permanent operation
  • the output of the air treatment device is with a first flow path of a recuperative heat recovery system and air handling unit hermetically separated from each other first and second flow paths, wherein the first flow path emitted at the output of the air treatment device supply air as cooled supply air to the interior of the tower and / or the Gives subassembly module and in the second flow path outside air (AL) is sucked by means of an additional fan and delivered to an exhaust air connection.
  • A outside air
  • a mechanical cooling device is additionally arranged in the flow path of the supply air to the cooled supply air.
  • the supply air duct is connected to a heat exchanger which emits heat energy taken up by the electrical and electronic units arranged in the unit module to the supply air flow of the first flow path leading into the interior of the tower, wherein the heat energy delivered by the heat exchanger to the supply air flow depends on the heat energy Temperature in the interior of the tower and / or the nacelle adjustable and at least one temperature in the interior of the tower and / or the nacelle detecting temperature sensor is connected to a control device.
  • the circulating air is conducted in the supply air and exhaust air ducts from the plate heat exchanger to and from the unit module, so that the circulating air flow is selectively guided via the air ducts in the individual floors of the unit module, the heat dissipated by the heat-emitting electrical and electronic units dissipated and thus prevents residual moisture and residual salt content in the Aggregate module can penetrate, the air ducts also cause a targeted air flow and cooling, so that the heat-emitting electrical and electronic units are effectively cooled regardless of their location.
  • a further high-performance filter is arranged in the circulating air flow path, with the salt particles, which could not be completely eliminated in the first treatment stage, additionally deposited.
  • the further high-performance filter is arranged in a bypass with two shutter flaps whose position determines the proportion of the circulating air flow as a function of a humidity measurement. which is passed through the arranged in the bypass channel high-performance filter.
  • the recirculation fan for continuously variable delivery of circulating air quantities to a regulated drive, creating a further possibility for temperature control is created.
  • a reduction in the air volume of the circulating air flow has the consequence, for example, that less energy is transferred through the plate heat exchanger to the outside air supply air flow.
  • both in the outside air supply air flow and in the recirculation air each consisting of an evaporator or cooler, condenser or reheat register and compressor dehumidification heat pump can be arranged, the recirculation dehumidifying heat pump preferably arranged in the exhaust duct of the circulating air in the flow direction in front of the high-performance filter is used to eliminate salt particles and aerosols in the circulating air stream, which may leak into the unit module, possibly through leaks, while mounting or the like.
  • an independent heating device preferably an electric heating coil, can be arranged in the supply air flow path of the air treatment device behind the plate heat exchanger and upstream of the high-performance filter.
  • a bypass in the flow path of the circulating air flow with controllable Bypassklap- pen and a bypass line for passing the circulating air flow to the high-performance filter and a bypass in the outside air supply air flow path with independently controllable bypass valves and a bypass line for passing the supply air flow to the high-performance filter can be set with a control device such a position that the air flows at favorable humidity values either through the high-performance filter or be guided over the bypass lines to the high-performance filters.
  • the provided in the flow path of the circulating air flow dehumidification heat pump which is arranged in front of the heat from the waste heat of the electrical and electronic units in the aggregate module heating device and consists of an evaporator / cooler, compressor, and a first capacitor, can arranged around a inillerluft- supply air second capacitor can be extended, which is associated with the first capacitor and with this common or mutually operable.
  • the dehumidifying heat pump disposed in the outside air supply air flow path consists of an evaporator / condenser, a compressor, a first condenser, and a second condenser with a reciprocal operation.
  • the dehumidification heat pump systems designed in this way in the circulating air and fresh air supply air flow cause an emergency heating, for example for frost-free maintenance of the air treatment device, or for additional desalination and dehumidification at low temperatures
  • Temperatures and downtimes of the wind energy plant since the Entfeuchtungstagepumpensysteme in outdoor air supply air and circulating air flow through a very high efficiency with lowest power consumption provide high heating power, whereas an electric heater with the same thermal output would cause more than five times the power consumption.
  • the energy output can be switched over or regulated from 0 to 100%, depending on the requirement and the heat requirement. Since the dehumidification heat pump system also has two condensers in the outdoor air supply air flow, the heat energy can be discharged in the air direction before or after the plate heat exchanger as required, and regulated from 0 to 100%.
  • a jet nozzle for blowing a Zu povertystromes is arranged in the entrance of the tower at high speed in the center of the tower diameter, whereby with the simple air treatment device, the improved air treatment device or the optimal air treatment device and optionally heated in the heat exchanger supply air targeted in the upper region of the tower and closer can be brought to the nacelle, the air jet at high speed on its flow path inducing permanent air from all sides of the tower, so that air stratification and temperature stratification torn and secondary flows are avoided.
  • the most centric arrangement of the jet nozzle avoids a distraction and leaning of the flow to the tower wall and thus the so-called Koander effect.
  • a nozzle or diffuser shape is chosen because it keeps the static pressure losses low.
  • the mechanical air conveyors can preferably with the waste heat of the unit module arranged in the heat-dissipating electrical and electronic units fed heating devices are connected, which is advantageous due to the Abkühl bines by the tower walls in conjunction with the long flow paths.
  • the temperatures in the entire tower can be made more uniform compared to a single central heating and influence the temperature condensation behavior in the tower advantageous.
  • an air treatment unit with recuperative heat recovery system and hermetically separated first and second flow paths are arranged, wherein the first flow path leads outside air to the exhaust air and the second flow path in the recirculation mode sucks incoming air and discharges as indirectly freely cooled supply air.
  • a mechanical refrigeration device can be arranged.
  • At least one speed increasing device preferably a fan and a nozzle, arranged in the tower, the air at high speed obliquely upwards, on the tower wall along upwards and in the tower a rotary motion or vortex flow generated, wherein the nozzle preferably has a round shape or a flat-jet shape.
  • Figure 1 is a trained according to the prior art conventional device for the air treatment and air flow of an offshore wind energy plant.
  • Fig. 2 is a schematic representation of the aggregates of a conventional
  • Air treatment or desalination apparatus for desalination of the sea air and for generating an overpressure in the interior of the tower of an offshore wind power plant;
  • Fig. 3 is a Mollier-h, x-diagram for humid air for explaining the receptivity of water in the air at different air temperatures;
  • Fig. 4 is a graph showing the corrosion rate of metals as a function of moisture film thickness
  • FIG. 6 shows a h, x diagram for humid air for illustrating the region of the "critical humidity" in connection with a fictitious weather bubble
  • FIG. 7 is a schematic representation of a simple air treatment system for aftertreatment and supplementary air treatment in an offshore wind power plant
  • Fig. 8 is a schematic representation of a portion of a tower of an offshore
  • FIG. 9 is a schematic representation of a portion of a tower of an offshore
  • FIG. 10 is a schematic representation of an improved air handling unit having a dehumidification heat pump and a high efficiency filter of the improved air handling system of FIG. 9;
  • FIG. 10 is a schematic representation of an improved air handling unit having a dehumidification heat pump and a high efficiency filter of the improved air handling system of FIG. 9;
  • Fig. 11 is a Mollier-h, x-diagram for humid air for explaining the improved air treatment system of Fig. 9;
  • FIGS. 12 and 13 show two embodiments of a combination of an improved air treatment device according to FIG. 10 with a conventional air treatment or desalination device;
  • FIG. 14 is a schematic representation of an optimized air treatment system for aftertreatment and supplementary air treatment with an optimal air treatment device in an offshore wind
  • FIG. 15 shows an air guidance and system diagram of a first embodiment of an optimal air treatment device for the optimized air treatment system according to FIG. 14;
  • FIG. 15 shows an air guidance and system diagram of a first embodiment of an optimal air treatment device for the optimized air treatment system according to FIG. 14;
  • FIG. 16 shows a longitudinal section through the housing of the first embodiment of the optimal air treatment device according to FIG. 15;
  • FIG. 17 shows an air guidance and system diagram of a second embodiment of an optimal air treatment device for the optimized air treatment system according to FIG. 14;
  • FIG. 18 shows an air guidance and system diagram of a third embodiment of an optimal air treatment device for the optimized air treatment system according to FIG. 14;
  • FIG. 19 shows a longitudinal section through the housing of the third embodiment of the optimal air treatment device according to FIG. 18;
  • FIG. 23 shows a Mollier-h, x diagram for outside air and return air (circulating air) in summer and winter operation of an optimum air treatment device according to FIG. 22;
  • FIGS. 24 to 28 air guiding and system diagrams of further embodiments of an optimal air treatment device for the optimized air treatment system according to FIG. 14;
  • FIGS. 29 to 31 show three embodiments of a combination of the optimal air treatment device according to FIG. 28 with the units of a conventional air conditioning or desalination apparatus;
  • FIG. 32 shows an offshore wind power plant with an optimized air treatment system and a reheating coil or heat exchanger and a jet nozzle for blowing a supply air flow into the tower of the offshore wind power plant at high speed;
  • Fig. 33 is a Mollier-h, x diagram for explaining the effect of the optimized one
  • Air treatment system with the optimal air treatment device
  • FIG. 34 shows an offshore wind power plant with several intermediate decks and speed-increasing devices designed as a nozzle or diffuser;
  • FIG. 35 shows a detailed representation of an intermediate deck with bypass flows and a nozzle with a mechanical air delivery device
  • FIG. Fig. 36 is a schematic representation of an air treatment system for a
  • Offshore wind energy plant in conjunction with a conventional air treatment or desalination plant
  • FIG. 37 shows an offshore wind power plant with mechanical air conveyors and heaters in several intermediate decks
  • 38 shows a detailed representation of an intermediate deck above an aggregate module with a nozzle with a fan, a high-performance filter and a heat exchanger;
  • FIG. 39 shows a schematic representation of an optimized air treatment system with a combination of a conventional air treatment and / or desalination device, an improved air treatment device and a plate heat exchanger for free, indirect cooling of the supply air flow delivered into the tower of a wind energy installation;
  • Fig. 40 is a schematic representation as in Figure 39 with an additional mechanical cooling of the supply air flow in the tower of the wind energy plant.
  • 41 shows a schematic representation of an optimized air treatment system for partial areas of a wind power plant for additional or independent cooling of units
  • FIG. 42 shows a schematic representation as in FIG. 41 with an additional mechanical cooling
  • Fig. 43 is a schematic representation of an air treatment system for a
  • Fig. 44 is a schematic representation of FIG. 43 with registered therein
  • Temperature examples for the area of the German North Sea and Fig. 45 is a schematic representation of the increase of the cooling effect by the
  • the outside air AL sucked from the environment of an offshore wind energy installation 1 according to FIG. 1 is roughly desalinated and dehumidified and continues to flow in an uncontrolled, turbulent and free air flow moist and salzaerosols containing supply air ZL on the arranged in the aggregate module 15 of the tower 10 electrical and electronic units 16 in the upper part of the tower 10 to the nacelle 1 1.
  • the residual salt content of the Zu poverty ZL flowing through the aggregate module 15 and the tower and the nacelle is thereby a hundred times greater than the desired value, so that the electrical and electronic units 16 and in the tower 10 and the nacelle 11 arranged devices and inner walls of the tower 10 are exposed to strong corrosion due to the influence of the salt and the residual moisture of the supply air ZL.
  • the moist and saline outside air AL drawn in via the air inlet opening 14 from the environment of the tower 10 is roughly desalinated in the air treatment or desalination apparatus 2 according to FIG and dehumidifies.
  • the roughly desalinated and dehumidified outside air AL is delivered to a simple air treatment device 3 in which the outside air AL is heated and the salt aerosols crystallized thereby into particles in the outside air AL are filtered out.
  • the supply air ZL discharged by the air treatment device 3 flows through the aggregate module 15 in free, uncontrolled flow, absorbs the radiant heat emitted by the electrical and electronic units 16 in the aggregate module 15 and exits the aggregate module 15 as heated supply air ZL 'in an uncontrolled, spinning air flow in the upper part of the tower 10 and in the gondola 11 a.
  • the supply air ZL ' flows through the overpressure generated by the outside air fan 25 in the air treatment or desalination unit 2 according to FIG. 2 as exhaust air FL into the environment of the offshore wind power plant 1.
  • the supply air ZL flows past the electrical and electronic units 16, absorbs the heat energy emitted by the electrical and electronic units 16 and enters the upper part of the tower 10 above the unit module 15 as heated supply air ZL ' whereupon the heated supply air ZL 'ascends as an uncontrolled, turbulent flow to the nacelle 11.
  • the simple air treatment device 3 is based on the finding that salt aerosols crystallize to particles at a relative humidity of the outside air of less than 40%. If the outside air AL is now heated to such an extent that the relative humidity characteristic of 40% in the Mollier-h, x-diagram is reached, then the salt aerosols crystallized into particles can be deposited as salt particles in the high-performance filter 32 arranged downstream of the heating device 31.
  • the heating device 31 is supplied with energy from the waste heat of the electrical and electronic units 16 in the unit module 15, for example by liquid cooling of at least part of the electrical and electronic units 16 and re-cooling of the heat absorbed in the cooling liquid in a heater 31 designed as an evaporator.
  • the above-described simple air treatment device 3 ensures a significant reduction of the residual salt content and thus significantly reduces the risk of corrosion in the unit module 15 and inside the tower 10 and in the nacelle 1 1, but can not ensure under all climatic conditions and year-round that the air flow in the Aggregate module 15 and inside the tower 10 and the nacelle 1 1 is maintained in such a way that on the one hand, the heat emitted by the electrical and electronic units 16 heat is dissipated sufficiently safe and on the other hand, the risk of corrosion inside the tower 10 and the nacelle. 1 1 can be excluded.
  • the wind power plant is not in operation for many hours of the year, for example during storms, light winds, accidents and maintenance.
  • an emergency operation is required that can be ensured only insufficiently with the simple air treatment device 3 by, for example, the air heater 31 of the simple air treatment device 3 is connected to an electric afterheating device, which is fed in emergency operation from the supply network to which the wind energy system emits electrical energy in normal operation.
  • thermodynamic treatment of the outside air AL or supply air ZL is not possible, especially since the available heat from the heat radiation of the electrical and electronic units 16 and the energy from the electric and electronic units 16 to a cooling liquid for heat dissipation and powering the air heater 31 and an evaporator of the simple air treatment device 3 between full load and partial load fluctuations and in emergency mode, ie at standstill of the wind energy plant, not available at all are.
  • FIGS. 5 to 6 show an improved air treatment device 4, which is described in more detail below and explained in its function.
  • the improved air treatment device 4 contains an evaporator 41, to which the desalinated and dehumidified outside air AL discharged from the conventional air treatment device 2 is sucked in via the air inlet opening 14 from the environment of the tower 10 as moist and saline outside air AL Air treatment or desalination unit 2 as shown in FIG. 2 was partially desalinated and dehumidified.
  • the improved air treatment device 4 includes a condenser or reheat coil 43 and a compressor 42, which together with the evaporator 41 form a dehumidifying heat pump, and a high-efficiency filter 44 for salt separation.
  • the partially desalinated and dehumidified outside airflow AL discharged from the conventional treatment apparatus 2 is discharged from the outside air fan 25 arranged in the flow path of the outside air AL in the air conditioning or desalination apparatus 2 shown in FIG. 2 to the improved air handling unit 4 in which the outside air AL is supplied by means of the evaporator 41 is cooled to a lower level, wherein the absolute humidity of the outside air AL is lowered.
  • This process also ensures that the dehumidified and desalinated supply air ZL even at total recooling to the temperature value of the outside air AL due to cooling on the way from the unit module 15 to the nacelle 11 through the non-insulated steel walls of the tower 10 at any point in the interior of the tower 10 the low level of the dew point, d. H. a relative humidity of 100%, can reach.
  • the value of the relative humidity in the entire interior of the tower 10 is about 70% relative humidity, so that the risk of condensation in the entire wind energy plant and thus the risk of corrosion by reducing the moisture is significantly reduced.
  • the absolute humidity of the outside air AL is reduced to about 10 g / kg.
  • the relative humidity of the outside air is reduced to about 35%, so that the Salzaerosole contained in the outside air AL in We - Essentially crystallized and the crystallized salt aerosols and contained in the outside air AL salt particles in the high-performance filter 44 can be deposited.
  • the outside air AL dehumidified and desalinated in the air treatment device 4 is discharged into the interior of the tower 10 as supply air ZL to the unit module 15 and after passing through the unit module 15 and receiving the thermal energy emitted by the electric and electronic units 16 as heated supply air ZL '. give, by the inclusion of additional heat energy, a further increase in temperature compared to the temperature T13, which is associated with a further decrease in the relative humidity.
  • a temperature T21 of the outside air AL of 14 0 C is assumed.
  • the moist and saline outside air AL is cooled along the dew point line in the evaporator 41 to a temperature T22 of about 9 0 C and thereby lowered to an absolute humidity of about 7 g / kg.
  • T23 of about 25 0 C the relative humidity of the outside air is reduced to about 38% and the salt salts thus crystallized and contained in the outside air AL salt particles are in the high-performance filter 44th deposited.
  • a temperature T31 of the outside air AL of 7 ° C. is assumed.
  • the moist and salty outside air AL is cooled down along the dew point line in the evaporator 41 to a temperature T32 of approximately 2 ° C. and thereby to an absolute humidity of lowered about 4 g / kg.
  • T33 the relative humidity of the outside air is reduced to about 40% and the salt crystals so salted and salt particles contained in the outside air AL are in High-efficiency filter 44 deposited.
  • the fresh air AL dehumidified and desalinated in the improved air treatment device 4 is also supplied as supply air ZL to the unit module 15 and after passing through the unit module 15 and receiving the heat energy radiated by the electric and electronic units 16 as the heated supply air ZL 'discharged into the interior of the tower 10.
  • the dehumidified and desalinated in the air treatment device 4 outside air AL as supply air ZL to the unit module 15 and after flowing through the unit module 15 and receiving the radiated from the electrical and electronic units 16 thermal energy as heated supply air ZL 'in the interior of the tower 10 is delivered , wherein the absorption of additional heat energy, a further temperature increase compared to the temperatures T23, T33 and T43 takes place, which is associated with a further decrease in the relative humidity.
  • FIGS. 8 and 9 show two variants of a combination of an improved air treatment device 4 with a conventional air treatment device 2 and will be explained in more detail below.
  • the moist and saline outside air AL sucked in via the air inlet opening 14 from the environment of the tower 10 by means of the outside air fan 25 is not conducted via the conventional air treatment device 2 according to FIG. 2, but only via a first droplet separator 21 first simplified air treatment device 2 'and then supplied as dehumidified outside air AL to the evaporator 41 for cooling and dehumidifying.
  • the crystallized salt aerosols and salt particles contained in the outside air AL are deposited in the high-performance filter 44, wherein the air flow through the in this embodiment, preferably on the suction side of the reduced air treatment device 2 'and reduced to the mist eliminator 21 the improved air treatment device 4 is arranged and the dehumidified and desalinated supply air ZL and desalted in the high-performance filter 44 outside air AL as supply air ZL in free air flow to the unit module 15 and as heated supply air ZL 'in the interior of the tower 10 and the nacelle 11 is discharged.
  • the coalescence separators 22 and 23 according to FIG. 2 are omitted because the dehumidification heat pump formed by the evaporator or condenser 41, condenser or reheat register 43 and compressor 42 results in dehumidification and heating of the dehumidifying heat pump Outside air AL is carried out in such a way that first water and thus also salt sols are deposited and crystallize the remaining salt components after heating by means of the dehumidification heat pump, when a value of relative humidity of less than or equal to about 40% is reached. Subsequently, the high-performance filter 44 ensures the deposition of the crystallized salt.
  • FIG. 9 shows the arrangement of both the two mist eliminators 21, 24 and a coalescence separator 22 in an air treatment unit 2.
  • the outside air AL sucked from the environment by means of the outside air fan 25 is discharged via a first droplet separator 21, a coalescence - Separator 22 and a second droplet 24 of the air treatment unit 2 "passed there partially dehumidified and desalted and then supplied as partially dehumidified and desalinated outside air AL shown in Fig.
  • the outside air fan 25 arranged in FIGS. 8 and 9 on the suction side of the air treatment device 2 'or 2 "and the improved air treatment device 4 can alternatively also be on the pressure side, ie before the first droplet separator 21 of the air treatment device 2' or before the first droplet separator 21 of the improved air treatment apparatus 2 "or between the air treatment apparatus 2 'and 2" and the improved air treatment apparatus 4.
  • the arrangement of the outside air fan 25 on the suction side of the air treatment apparatus 2' and 2 "and the improved air treatment apparatus 4 has the substantial advantage that the outside air fan 25 is arranged not in humid air, but in relatively dry air, which is also free of salt, which has advantages with respect to the corrosion behavior of the outside air fan 25.
  • FIG. 10 an optimized air treatment system 6 with an optimal air treatment device 5 and air ducts 75, 76 shown in the unit module 15, with which under any climatic conditions, in the year-round operation and in emergency mode with stationary wind energy system optionally sucked on the air treatment unit 2 humid and salty outdoor air AL is dehumidified, filtered and desalted, a cooling of arranged in the unit module 15 heat-dissipating electrical and electronic units 16 is performed, a positive pressure in
  • the sucked in moist and saline outside air AL in the air treatment unit 2 is only partly or coarsely desalted and partially dehumidified, the still moist and salty outside air AL 'an optimal air treatment device 5 and supplied from this as dehumidified and desalinated supply air ZL guided through an inlet air duct 74 through the unit module 15, without coming into contact with the air in the unit module 15, and discharged above the unit module 15 to the overlying free space 100 of the upper part of the tower 10.
  • a Nachffyregister or heat exchanger 8 can be arranged with control valve, with which the temperature in the upper region of the tower 10 and in the nacelle 1 1 is controlled.
  • the heat exchanger 8 is fed from the waste heat of the heat generating electrical and electronic units 16 in the unit module 15.
  • the heat exchanger 8 can alternatively or optionally also be arranged directly in or on the optimized air treatment device 5 or at any other point in the supply air channel 74.
  • the effect and positive consequences of the heat exchanger 8 are that in order to avoid condensation within the tower 10 and the nacelle 1 1, the air is heated so far through the heat exchanger 8, i. a temperature increase is effected, that even by the cooling effect of the tower walls and a drop in temperature in the tower 10 and the nacelle 1 1, the dew point is not reached.
  • a sensor for the temperature measurement and control in the nacelle 1 1 is arranged in front of the air outlet due to the generated overpressure.
  • the second flow path leads in a closed circuit through the aggregate module 15 and delivers the heat energy absorbed by the heat emission of the electric and electronic units 16 via the air treatment device with recuperative heat recovery system 51 to the first flow path, from which, excluding the aggregate module 15 heated, dehumidified and desalted air with pressure to the interior 100 of the tower 10 and the nacelle 1 1 is discharged.
  • This ensures that the still contaminated with salt outside air AL 'no longer flows freely through the unit module 15 and thus the electrical and electronic units 16 can no longer contaminate.
  • the air treatment device 5 not only causes dehumidification and desalination of the discharged from the air treatment unit 2 outside air AL ', but also takes over the cooling of the unit module 15 by a targeted air extraction from the individual floors or platforms of the unit module 15 via recirculation air ducts 76 and a targeted air supply via Recirculation air supply ducts 75 in the individual floors or platforms of the unit module 15. If the supply air ZL (UL) the circulating air UL is not supplied to the individual floors of the unit module 15, but injected, for example, in the lower floor and deducted in the upper floor, so is a appropriate air duct between the floors of the unit module 15 is provided.
  • UL the supply air ZL
  • the energy is exchanged via the arranged in the optimized air treatment device 5 plate heat exchanger 51 between the outside air flow 1 and the guided in the air ducts 75, 76 circulating air flow UL.
  • the outside air flow AL 'or supply air flow ZL thus indirectly cools the recirculating air flow UL.
  • the circulating air flow UL the heat, which results from the surface heat output of the electrical and electronic units 16, to the supply air flow ZL, so that the heated supply air flow ZL "shown in FIG. 10 preheated in the upper tower 10 and thus in the nacelle 1 1.
  • additional reheating can take place through the optionally arranged heat exchanger 8.
  • the plate heat exchanger 51 in the optimized air treatment device 5 hermetically separates the outside air flow AL 'and inlet air flow ZL from the recirculating air flow UL and thus ensures that a free flow through the aggregate module 15 and thus contamination by salt-containing, moist outside air AL' can not take place.
  • the aggregate module 15 is located in a salt-free zone of the tower body.
  • the unit module 15 can also be arranged below the air inlet opening 14 for the outside air AL, so that the optimized air treatment device 5 delivers the heated and desalinated air directly to the upper, free part of the tower 10, while the circulating air flow UL into the below the optimized air treatment device 5 arranged unit module 15 is discharged, where the circulating air flow UL receives the output from the electrical and electronic units 16 heat and this via the plate heat exchanger 51 in the hermetically separated supply air flow ZL and thus in the optionally heated by the Nachsagenregister or the heat exchanger 8 supply air ZL "fed into the interior of the tower 10.
  • the optimized air treatment device 5 does not necessarily have to be arranged in the region of the aggregate module 15, but can be arranged at any other location, in particular because a targeted introduction of air into the unit module 15 and air extraction from the unit module 15 can be generated by air ducts. Also, the supply air duct 74 entered in FIG. 10 does not necessarily end at the upper deck of the unit module 15, but can also be extended beyond that into the interior of the tower 10.
  • the air treatment device 5 shown in Fig. 11 as an air flow and system schematic and in Fig. 12 in a longitudinal section through a corresponding air conditioner shows a housing 50 with an outside air opening for intake outside air AL, a supply air / pressure opening for delivering the heated supply air flow ZL to the part of the tower 10, which lies above or outside the aggregate module 15, and an exhaust / return air duct or channels 76 and a circulating air / supply air duct or channels 75, via which the circulated air is led into and out of the unit module 15.
  • a plate heat exchanger 51 is arranged with hermetically separated, in heat exchanging connection flow paths, of which the first flow path from the vicinity of the tower 10 via the air inlet opening 14 sucked outside air AL via an evaporator or cooler 53, the plate heat exchanger 51, a condenser or a reheat register 55 and the supply air / overpressure opening and the supply air duct 74 to the upper part of the tower 10, during the heat-exchanging connection with the first flow path stationary second flow path through a circulating air fan 56, is conducted in a closed circuit from the unit module 15 via the exhaust air / return air duct 76, the plate heat exchanger 51 and the circulating air / supply air duct 75 into the unit module 15 and the heat energy absorbed by the heat output of the electrical and electronic units 16 over the plate heat exchanger 51 outputs to the first flow path.
  • the first flow path leads via the supply air duct 74, excluding the unit module 15, the heated supply air ZL with overpressure to the interior of the tower
  • the plate heat exchanger 51 at the entrance of the cooled outside air AL 'bypass flaps 52 on the adjustment thus influence the energy exchange and thus on the temperature and / or humidity behavior of the air treatment device 5 can be taken.
  • the bypass flaps 52 of the plate heat exchanger 51 can be included in a temperature and humidity control of the optimized air treatment system 6.
  • the outside air fan 25 is not shown in FIGS. 11 and 12 according to the embodiments described above.
  • the arrangement of the outside air ventilator 25 on the suction side offers advantages , ie in the flow direction of the outside air AL to the supply air ZL behind the air treatment device 5, since it is here in dry, salt-free air, whereby the risk of corrosion is significantly reduced and only small demands on the material quality of the outside air fan 25 are to make allows the arrangement of the outside air fan 25 on the suction side placements of the outside air fan 25, which are possible and suitable from the unit module 15 over all intermediate decks of the tower 10 to the nacelle 1 1 as a site.
  • the air treatment device 5 comprises the dehumidifying heat pump formed by the evaporator or cooler 53 and the condenser or reheat register 55 and a compressor 54, which is designed such that a Dehumidification by 1 g / kg air or more is achieved. Subsequently, the temperature of the outside air AL 'increases after passing through the plate heat exchanger 51 to a correspondingly higher temperature in a favorable range of relative humidity, i. as far away from the dew point as possible.
  • a dehumidification of 1 g / kg already causes, when cooling down the supply air ZL blown into the interior of the tower 10 on the way to the outlet opening 13 in the nacelle 1 1 on the value of the outside air temperature, the dew point line, ie the line 100% humidity in Mollier-h, x-diagram, is not reached, so that there is no risk of condensation inside the tower 10 and the nacelle 1 1.
  • Higher dehumidification than 1 g / kg for example by arranging an additional electric heater, causes the distance from the dew point line in the Mollier-h, x diagram is further increased, but causes additional energy costs. According to FIG.
  • the outside air is additionally heated immediately after exiting from the plate heat exchanger 51 with the energy from the dehumidification process via the condenser or the reheat register 55, which in turn has an even more favorable, namely a lower value in the relative Moisture causes.
  • the Mollier-h, x-diagram shown in FIG. 19 shows that the air flowing through the tower 10 and the nacelle 11 and cooled again via the tower walls, even with a one hundred percent cooling effect, reaches the low level achieved by this process Dew point can not fall below. At best, the cooling air flow can rise to a relative humidity of 80% at most.
  • the arrangement of the evaporator 53 and condenser 55 is not necessarily required at the air inlet or outlet of the plate heat exchanger 51, but may also be located somewhere within the duct system of the injected into the tower 10 Zu Kunststoffstromes ZL, d. h., Are provided within the supply air duct 74.
  • the condenser 55 is not arranged in the flow direction after the plate heat exchanger 51, but, for example, immediately after the evaporator 53, then the dehumidification purpose, d. h., the moisture reduction in the same way.
  • the immediate reheating (Reheat) would reduce the cooling effect of the circulating air flow UL, which would be technically disadvantageous, but would not affect the functioning of the dehumidification heat pump.
  • the optimum air handling systems 6 shown in FIGS. 10 to 29 may include air handling and dynamics elements and components in the tower 10, such as the arrangement of nozzles, heaters, other re-generation fans, and the like, also in conjunction with the above described improved air treatment device 4 are used.
  • the air ducts 75, 76 also cause a targeted air flow and targeted cooling, so that the heat-emitting electrical and electronic units 16 are effectively cooled regardless of their location.
  • the bypass flap 52 provided on the plate heat exchanger 51 also makes it possible to variably control the energy exchange for temperature and / or humidity control. While the outside supply air flow is conveyed via the outside air fan 25, the independent recirculation fan 56 generates the circulating air flow, wherein the variable speed circulating air fan 56 generates variable volume flows of the circulating air flow, thus also the heat transfer in the plate heat exchanger 51 and thus the temperature and / or Humidity can be controlled or regulated.
  • FIG. 13 shows a variant of the configuration of the optimal air treatment device 5 with a reheat register 62 arranged in the exhaust air / return air line 76 of the circulating air UL in the form of a condenser, in the case of heating demand in the aggregate module 15, for example in the winter months at low or too low Temperatures and / or emergency operation at standstill of the offshore wind power plant, is switched by the capacitor 55, so that the dehumidification heat pump formed by the evaporator or condenser 53, condenser or reheat register 55 and compressor 54 in outside air supply air flow AL / ZL heats the supply air ZL (UL) of the circulating air UL of the second flow path, which is delivered to the unit module 15.
  • the energy for this heating operation is supplied by other offshore wind power plants operated in the network.
  • salt is in humidities> 70% in the liquid state. At moisture levels of 40 to 70% results in a mixed form. At relative humidities less than 40%, salt is present in bound particles (as dust, so to speak). In the cold winter months weather conditions can occur, which reach due to low temperatures, in particular (but also by the heating of the air) humidity values, which are below 40%.
  • an embodiment of the air treatment device according to FIG. 1 In order to prevent uncleaned air or air having an inadmissibly high salt content from entering into the unit module 15 as a result of leaks or other circumstances, an embodiment of the air treatment device according to FIG.
  • the high-performance filter 57 and the recirculation fan 56 another high-performance filter 61 is used in the circulating air flow UL, with the salt particles, which could not be completely eliminated in the first treatment stage, additionally deposited.
  • FIG. 15 shows a schematic longitudinal section through the housing 50 of the air treatment device 5 illustrated in FIG. 14 as an air-guiding and system diagram.
  • the high-performance filter 61 in the embodiment of the air treatment device of FIG. 16 in a bypass 60 to optional switching on or off, for example, depending on the humidity arranged.
  • the bypass 60 has two shutter flaps 602, 603 which, depending on a moisture measurement, determine the proportion of the circulating air flow UL, which is conducted via the bypass channel 601 and thus through the high-efficiency filter 61.
  • a similar bypass can also be provided in the flow path of the outside air supply air flow in the flow direction behind the plate heat exchanger 51 in conjunction with the high-performance filter 57.
  • the embodiment of an optimum air treatment device 5 shown in FIG. 17 differs from the air treatment device 5 according to FIG. 14 in that the dehumidification heat pump has two capacitors or reheat registers 55 and 59, of which a first capacitor 55 in FIG Flow direction of the outside air supply air flow in front of the plate heat exchanger 51 and the second capacitor 59 is arranged in the flow direction of the outside air supply air flow to the plate heat exchanger 51.
  • the dehumidification heat pump has two capacitors or reheat registers 55 and 59, of which a first capacitor 55 in FIG Flow direction of the outside air supply air flow in front of the plate heat exchanger 51 and the second capacitor 59 is arranged in the flow direction of the outside air supply air flow to the plate heat exchanger 51.
  • This mutual circuit of the capacitors 55, 59 has the advantage that the different requirements between summer and winter operation can be better met. Since the efficiency of the plate heat exchanger 51 and its heat transfer is determined by the temperature difference, the first Capacitor 55 is preferably used in winter, while second capacitor 63 is preferably used in summer. Depending on the respective requirements, both capacitors 55, 59 can be operated in partial load operation, wherein both capacitors 55 and 59 are automatically controlled in mutual operation or with variable partial loads.
  • Another possibility for temperature control is to provide the recirculation fan 56 with a regulated drive, so that it can promote infinitely variable air volumes.
  • a reduction of the air volume of the circulating air flow UL has the consequence, for example, that less energy is transferred through the plate heat exchanger 51 to the outside air supply air flow.
  • the air treatment device 5 in addition to the bypass flaps 52 on the plate heat exchanger 51 and the mutually controllable capacitors 55, 59, a further influencing variable for temperature and humidity control.
  • the air treatment device has a dehumidification heat pump system from an evaporator or cooler 53, condenser or reheat register 55 and compressor 54 as well as a dehumidification heat pump system from an evaporator or cooler 62, condenser or reheat in the circulating air flow Register 64 and compressor 63, which is arranged in the exhaust air duct 76 of the circulating air UL in the flow direction in front of the high-performance filter 61.
  • the mode of operation of the air treatment device according to FIG. 18 during summer and winter operation will be explained with reference to the Mollier-h, x diagram shown in FIG. 19.
  • the numeral 1 indicates the humidity and temperature conditions of the outside air in summer, the numeral 2 of the return air or circulating air in summer, the numeral 3 of the outside air in winter and the numeral 4 of the return air / circulating air in winter.
  • both for the outside air AL and for the recirculating air UL cooling takes place with simultaneous dehumidification.
  • reheating takes place both for the outside air AL and for the circulated air UL (reheat) through the condenser 55 or 59 according to the dehumidification heat pump principle.
  • the third step takes place for the outside air AL further heating by the heat transfer from the warmer, guided over the plate heat exchanger 51 circulating air flow UL.
  • Tig takes place in the third step for the circulating air flow UL, which is in the relatively dry range, that is below or around the 40% relative humidity line, the filtering and thus the elimination of salt particles from the recirculating air flow UL.
  • the filtering and elimination of the salt particles from the outside air supply air flow takes place after the outside air flow has absorbed heat from the transfer of the plate heat exchanger 51.
  • the Mollier-h, x-diagram according to FIG. 19 shows that the outside air supply air flow both in summer and winter operation respectively reaches and even falls below the relative minimum moisture content of less than or equal to approximately 40%, which is the The prerequisite for this is that salt particles are formed from the aerosols, which are precipitated in the high-performance filters 57, 61.
  • FIG. 20 air guide and system diagram of another embodiment of the optimal air treatment device 5 differs from the embodiment of FIG. 8 by the arrangement of a bypass 70, which leads from Zu povertyka- channel 74 and thus from the supply air ZL to the recirculating air UL, where it is connected between the dehumidification heat pump system formed by the evaporator or condenser 62, condenser or reheat register 64, compressor 63 and the high-efficiency filter 61 for overpressure maintenance in the circulating air flow UL.
  • a bypass 70 which leads from Zu povertyka- channel 74 and thus from the supply air ZL to the recirculating air UL, where it is connected between the dehumidification heat pump system formed by the evaporator or condenser 62, condenser or reheat register 64, compressor 63 and the high-efficiency filter 61 for overpressure maintenance in the circulating air flow UL.
  • the air treatment device 5 it is achieved that the circulating air UL flowing through the unit module 15 is not contaminated by streams from other areas of the wind energy installation with salty air.
  • the required amount of bypass air is very small and does not significantly affect the moisture content of the circulating air UL and only prevents negative flows from the area of the tower 10 of the wind turbine or the air inlet opening 14 in the aggregate module 15 penetrate, so that the required amount of air is only slightly.
  • the guided through the bypass 70 circulating air part is removed from the supply air flow ZL, which has already absorbed energy in the flow through the plate heat exchanger 51.
  • the supply of the bypass air flow to the circulating air UL can be arranged at any point of the air duct system, for example, the bypass air flow can also flow directly into the unit module 15 without air ducts.
  • FIGS. 21 to 27 show further exemplary embodiments of an optimal air treatment device 5 of an optimized air treatment system for normal operation and emergency operation 6, which can be selected adapted to the respective requirements such as environmental conditions, size and power of the wind energy installation, investment costs and the like.
  • the operation common to these embodiments will be described in more detail following the description of the Lucas Offices- and system schemes of FIGS. 21 to 27.
  • FIG. 21 differs from the air treatment device of FIG. 20 by the additional arrangement of an independent heater 58, preferably an electric heater, in the supply air flow path ZL behind the plate heat exchanger 51 and in front of the high-performance filter 57 of Air treatment device 5.
  • an independent heater 58 preferably an electric heater
  • a bypass 701 branches off from the supply air duct 74 from the supply air ZL to the unit module 15 or optionally via the bypass 702 to the circulating air flow UL, whereby both bypass guides are controlled via a motorized bypass flap 700, so that the supply air portion for overpressure control in the unit module 15 can be regulated ,
  • the evaporator 53 of the outside air dehumidification heat pump system preferably has a defrosting device, so that the entire power of the evaporator 53 is provided by two separate evaporator systems.
  • a division of the condenser of the outside air dehumidification heat pump system into two capacitors or reheat Register 55 and 59 are provided, of which the first capacitor 55 is arranged in the flow direction of the outside air supply air flow in front of the plate heat exchanger 51 and the second condenser 59 in the flow direction of the outside air supply air flow to the plate heat exchanger 51.
  • the supply air flow ZL can be further heated after the plate heat exchanger 51.
  • the illustrated in Fig. 23 air guide and system diagram of another embodiment of the invention optimal air treatment device 5 differs from the embodiment shown in FIG. 22 by the optional arrangement of a bypass 71 in the flow path of the circulating air flow UL and a bypass 72 in the outside air supply air Flow path AL / ZL.
  • the bypass 71 in the circulating air flow path UL has bypass flaps 71 1, 712 and a bypass line 713, while the bypass 72 in the outside air supply air flow path AL / ZL contains bypass flaps 721, 722 and a bypass line 723 from the outside air AL to the inlet air ZL.
  • bypasses 71, 72 provided in the outside air supply air flow AL / ZL and in the recirculation flow UL make it possible to pass the air streams past the high-performance filters 57, 61 via the bypass lines 713 or 723 if the relative humidity of less than or equal to approximately 40% does not pass can be reached or held.
  • the independently controllable bypass flaps 71 1, 7182 and 721, 722 can be adjusted by a control device in the respective required position, so that the air flows at low humidity either the high-performance filter 57, 61 or via the bypass lines 713, 723 to the high-performance filters 57th 61 are passed by.
  • the air duct and system diagram of a further embodiment of the optimum air treatment device 5 according to the invention shown in FIG. 24 differs from the air treatment devices described above by the additional arrangement of dehumidification heat pump systems in the outside air supply air flow AL / ZL and in the recirculation air flow UL. That in the flow path of the circulating air stream UL arranged in front of the heating device 65 fed from the waste heat of the electrical and electronic units 16 in the unit module 15 dehumidifying heat pump system consists of the evaporator / condenser 62, compressor 63 and a first capacitor 64.
  • the dehumidifying heat pump system consisting of the compressor 54 and a first capacitor / reheat register 55 or a second capacitor / reheat register 59 with mutual operation.
  • a second condenser / reheat register 66 connected to the dehumidification heat pump system arranged in the circulating air flow UL is assigned to the first condenser / reheat register 65 and can be operated together or alternately therewith.
  • the evaporator 53 arranged in the dehumidification heat pump system of the outside air supply air flow AL / ZL preferably has a defrosting device, for which reason the entire power of the evaporator 53 is applied by two optionally separate evaporator parts.
  • the air treatment device shown in FIG. 24 with dehumidification heat pump systems in the circulating air flow UL and outside air supply air AL / ZL can be used as emergency heating, for example to keep the air treatment device 5 free of frost, or for additional desalination and dehumidification at low temperatures and downtimes of the wind energy plant.
  • the dehumidification heat pump systems in the fresh air supply air flow AL / ZL and recirculated air flow UL offer a high heating efficiency through very high efficiency with lowest power consumption, whereas an electric heating coil would cause more than five times the electricity consumption with the same heat output.
  • the energy output can be switched or regulated from 0 to 100%, depending on the requirement and the heat requirement.
  • the dehumidification heat pump system in the outside air supply air flow AL / ZL also has two condensers 55, 59, so that the heat energy can be discharged as required in the direction of air before or after the plate heat exchanger 51 and controlled from 0 to 100%.
  • FIGS. 25 to 27 Various variants of a combination of the air treatment device 5 according to FIG. 24 with a conventional air treatment device 2 according to FIG. 2 are illustrated in FIGS. 25 to 27.
  • the conventional air treatment device 2 consists of a first droplet separator 21, a coalescence separator 22 and a second droplet separator 24, which are arranged in the outside air flow AL between the air inlet opening and the optimal air treatment device 5.
  • the outside air fan 25 is arranged on the pressure side of the air treatment device 5 between the first droplet separator 21 and the coalescence separator 22.
  • outside air fan 25 shows in an alternative embodiment the arrangement of the outside air fan 25 in a dashed line on the suction side of the air treatment device 5, where the outside air fan 25 is not in moist, salty or only roughly dehumidified and desalinated outside air AL, but in dry, salt-free supply air. which considerably reduces the risk of corrosion of the outside air fan 25 and thus reduces demands on the material quality of the outside air fan 25 arranged on the suction side as well as other components which can be arranged either in the air flow direction in front of or behind the air treatment device 5. This is associated with a much cheaper construction of the optimized air treatment system.
  • the embodiment according to FIG. 26 differs from the arrangement according to FIG. 25 in that the outside air fan 25 is arranged on the suction side of the air treatment device 5.
  • the air treatment device 2 only consists of a mist eliminator 21, which is arranged on the suction side of the outside air fan 25, which in turn is arranged on the pressure side of the air treatment device 5.
  • the Koaleszenzabscheider 22 of the arrangement according to FIGS. 25 and 26 has been removed here, since its task is taken over by the air treatment device 5 with.
  • the components used in the optimized air treatment system 6, such as dehumidification heat pump systems (evaporator, condenser / reheat, heating coil, etc.) can be arbitrarily arranged and combined with each other for functional reasons or due to system or process conditions both in the flow direction before and after the plate heat exchanger 51.
  • the capacitors / reheat registers can be arranged both in the outside air flow AL and in the recirculation air flow UL and can be connected in any way with the dehumidification heat pump systems, depending on where the output from the electrical and electronic units 16 heat their best effect achieved by switching and / or step-affected or continuous control.
  • the above-described optimized air treatment systems 6 only exemplify some of many possible arrangements.
  • the optimal air treatment device 5 of an optimized air treatment system 6, which is intended and suitable for both normal operation and emergency operation, shown in FIGS. 10 to 27, has over the simple air treatment device 3 according to FIGS. 3 and 4 and the improved air treatment device 4 according to FIGS. 5 to 9 the following features and functions:
  • the outside air AL is transferred from the outside air fan 25 of the conventional air treatment device 2 to the air treatment device 5 and flows through first the evaporator 53, which has the following features or functions:
  • the evaporator 53 is preferably equipped with a defrosting device, since in the offshore region at low temperatures and high humidity in the freezing point and below there is a risk of icing due to the low evaporation temperature.
  • Deicing devices are known from the dehumidification heat pump design and therefore require no further description.
  • the evaporator with de-icing function 53 is designed in two parts for a partial load operation;
  • the evaporator 53 always operates when the inlet temperature, i. the outside temperature, at the dew point line, i. at 100% relative humidity, and thus an increased risk of condensation within the wind turbine can occur, a temperature drop along the dew point line and thereby eliminates water. This results in a reduction of the absolute humidity, so that the risk of condensation is dispelled.
  • a reduction in the relative humidity is sought in such a way that in conjunction with the condenser or the reheat device 55 and optionally by supplemental heaters on the entire route of the flow path of the supply air to the nacelle 1 1 and within the nacelle 11 even at total Recooling of the supply air flow as a whole or in places by the enormous area of the supply air
  • the dehumidification heat pump does not necessarily have to be operated in this weather situation, but merely optionally fulfills an additional purpose, namely the heating of the air to temperature ranges which crystallize the salt dissolved in aerosols, which occurs when the 40% moisture line is reached effective filtering possible.
  • the compressor 54 is connected to the evaporator 53 and the condenser 55 via piping and controls, and may be inside or outside the airflow.
  • the outside air AL flows through the condenser or the reheat register 55 and is reheated there in a first stage. Subsequently, the outside air flow AL receives further heat energy during the flow through the plate heat exchanger 51, which is discharged from the exhaust air of the circulating air flow UL. In this case, the plate heat exchanger 51 hermetically separates the outside air flow AL from the recirculating air flow UL.
  • the supply air flow has reached a temperature under normal operating conditions, which is less than or equal to about 40% relative humidity in the humidity range.
  • the saline sols are crystallized by this process and can be deposited by the redesigned high performance filter 57.
  • an additional heating device according to the optimal air treatment devices 5 shown in FIGS. 21 to 27 is provided, which is preferably an electric heater because heating must be provided especially in emergency mode.
  • a plurality of heating devices can be provided, which are fed, for example, in normal operation from the waste heat of the electrical and electronic units 16 in the unit module 15, in conjunction with the arrangement of an additional electrical heating device.
  • the temperature and humidity values can be influenced by means of the plate heat exchanger 51, which is preferably provided with bypass flaps 52, in conjunction with a control device of the optimum air treatment device 5, because variable amounts of energy are available for energy exchange or energy transfer.
  • the dehumidified and desalinated supply air ZL leaving the high-efficiency filter 59 can be led via the supply air duct 74 through the unit module 15 into the tower 10 and to the nacelle 11, the risk of condensation and increased corrosion within the tower 10 and the nacelle 11 being caused by salzerosols eliminated. Further measures for air treatment and air flow in the tower 10 and in the nacelle 1 1 will be described with reference to FIGS. 28 to 34.
  • the controllable circulating air fan 56 can be reduced to a reduced volume flow, which is a variable process in Dependent on the temperature and humidity setpoints can be performed. At a lower volume flow both a higher exhaust air temperature and a lower relative humidity of the circulating air UL are achieved;
  • an additional heater 65 is provided in the embodiments of FIGS. 21 to 27, for example, from the waste heat of the electrical and electronic units 16 is fed in the unit module 15 and which heats the air of the exhaust air flow Ab (UL) of the circulating air UL in conjunction with a control valve to the required temperature.
  • This device is also provided for safety reasons, so that the temperature does not decrease uncontrollably by external influences and thus the required humidity of less than or equal to about 40% relative humidity can be achieved even in such weather conditions.
  • the exhaust air flow Ab (UL) of the circulated air UL After the exhaust air flow Ab (UL) of the circulated air UL has reached the required temperature and has been purified by the high-efficiency fine filter 61 provided in the circulating air flow path, the exhaust air Ab (UL) flows through the plate heat exchanger 51 and indirectly supplies the heat energy to the outside air Supply air flow AL / ZL.
  • the infinitely variable circulating air fan 56 now conveys the circulating air flow UL as the supply air flow ZL (UL) to the unit module 15, optionally into the individual levels of the unit module 15.
  • the outside air dehumidification heat pump to a second capacitor, which is arranged in the outside air supply air flow AL / ZL after exiting the plate heat exchanger 51.
  • This second capacitor or reheat register is provided, to the energy from the dehumidification heat pump system by switching between the first capacitor and the second capacitor as a function of the outside temperature and the required Enticarmungs intricate for cooling the arranged in the unit module 15 electrical and electronic units 16 in conjunction with the set for the aggregate module 15 limit to transmit the temperature with the most favorable effect.
  • variable amounts of air both the outside air AL to supply air ZL and the circulating air UL the optimized air treatment system 6 depending on the parameters of the outside air, such as outside air temperature, humidity and salinity of the outside air AL and depending on the required in the unit module 15 Entracermungshunt and an emergency heating be significantly affected when the wind energy plant is at a standstill.
  • variable air volumes of the outside air supply air or the circulating air is a significant factor on the energy consumption or energy costs given as a reduction of the outdoor air supply air and recirculated air quantities in the lowered operation with appropriate weather conditions and lower heat loads in Aggregate module also saves energy costs.
  • Switching between the two capacitors of the fresh air dehumidification heat pump fulfills the following tasks:
  • the first condenser is preferably to be used in winter, while the second condenser is preferably used in the summer.
  • both capacitors can also be operated in partial load operation, for which purpose both capacitors are steplessly regulated automatically with alternating, variable partial powers.
  • the optimized air treatment system 6 realizes an emergency operation, which is given for example in light wind, storm or accident or during maintenance of the wind turbine.
  • an emergency operation which is given for example in light wind, storm or accident or during maintenance of the wind turbine.
  • studies on the basis of wind and weather data for Heligoland have shown that a wind energy plant is not in operation for more than 2000 hours per year due to weak winds or strong winds.
  • the wind energy plant provides no energy and all units that need to be operated for the safety and protection of the wind turbine, are fed from the normal power grid, in which the wind turbine feeds energy in normal operation.
  • the power grid provides only limited energy and, as a rule, no waste heat for heating the systems and facilities of the wind power plant.
  • the optimized air treatment system 6 works in the emergency mode in principle as described above in normal operation, but with the following special features, since energy is available only to a limited extent:
  • heating devices 58, 65 can not be fed from the waste heat of the electrical or electronic units 16, there is no useful energy exchange in the circulated air and fresh air supply air flows through the plate heat exchanger 51, since there is no heat transfer;
  • the circulating air fan 56 stands still and does not convey circulating air, so that no circulating air flow flows through the unit module 15;
  • the outside air dehumidification heat pump is in operation, cools, dehumidifies and heats the outside air flow AL, but can not reach the 40% humidity line in every weather situation;
  • - For safety and residual reheating with a small amount of energy is preferably an electric heater with feed from the mains switched on and causes an increase in the temperature of the supply air, so that the wetness of 40% is achieved and the crystallized salt through the high-performance filter 57 in the supply air can be deposited.
  • the supply air flow ZL guided via the supply air duct 74 releases a small proportion of the air volume via the bypass 70 to the unit module 15 for overpressure maintenance and for reducing the moisture content of the circulating air.
  • the bypass flap 700 ( Figures 21 to 23) is opened and regulated to a certain, usually small amount of air.
  • the bypass air quantity can preferably also be introduced via the exhaust air of the circulating air flow into the unit module 15, namely via the connection between the bypass and the exhaust air of the circulating air according to FIGS. 21 to 23. Due to the above measures, condensation of the supply air ZL or circulating air UL can occur neither in the unit module 15, nor in the tower 10 or in the nacelle 11.
  • the evaporator 53 of the outside air dehumidifying heat pump can be equipped with a defrosting function for a partial load operation.
  • the entire evaporator capacity is divided into two evaporators with separate injection and separate expansion valve and separate shut-off valves via the air inlet cross-section at the respective evaporator.
  • the butterfly valves can optionally be opened or closed alternately, with both butterfly valves are open during normal operation, so that one half of the evaporator makes the cooling and / or dehumidification and the other half is de-iced with a closed butterfly valve by heating gas injection.
  • the embodiment shown in FIG. 28 of a device for aftertreatment, supplementary air treatment and targeted air guidance of the different air streams in a further supplement to the reheater or heat exchanger 8 according to FIG. 10 has a jet nozzle 80 for blowing the supply air flow ZL into the inlet of the Tower 10 at high speed, which is advantageously located in the center of the tower diameter.
  • the supply air flow ZL heated in the simple air treatment device 3, the improved air treatment device 4 or optimum air treatment device 5 and possibly in the heat exchanger 8 can be selectively guided into the upper region of the tower 10 and closer to the nacelle 11.
  • the air jet ZL '"at high speed induces permanent air LS on all sides of the tower 10 along its flow path, tearing open air layers and temperature stratifications and preventing secondary flows.
  • the most centric arrangement of the jet nozzle 80 avoids deflecting and leaning the flow to the tower wall and thus the so-called Coanda effect.
  • a nozzle or diffuser shape is chosen because it keeps the static pressure losses low.
  • Fig. 28 the outside air AL, the free supply air flow ZL '"in the tower 10, the exhaust air FL from the nacelle 1 1, the conventional air treatment unit 2 for desalination and pre-dehumidification and the optimal air treatment device 5 for air treatment with plate heat exchanger and dehumidification heat pump, the supply air - Overpressure air duct in the supply air duct 74 through the unit module 15, and the recirculating air UL for targeted extraction possibly with duct system and possibly with volumetric flow controllers and targeted supply air duct with duct system and possibly with volume flow regulators and an optional saucetau- shear 8 for heating the Zu poverty ZL '"in the tower 10 and the nacelle 1 1 shown.
  • the effect of the optimized air treatment system 6 with the optimum air treatment device will be explained with reference to the Mollier-h, x diagram shown in FIG. 29.
  • the sucked outside air is passed through the evaporator 53 and thereby cooled to about 4 ° C at a constant relative humidity according to the arrow A.
  • the supply air is heated according to the arrow C to about 27 ° C and as supply air via the supply air duct 6 in the upper part of the tower 10, ie, outside the unit module 15 in the interior of the tower 10 and the overhead gondola 1 1 blown.
  • the injected supply air is cooled to a maximum of 7 ° C at a maximum of 80% relative humidity according to the arrow D, which ensures that the dew point can not be achieved and condensation can not occur.
  • the arrow F denotes the direction of action of the partial pressure, which causes a reduction of the moisture content in the circulating air flow and thus a drying in the aggregate module 15 and thus a favorable flow always to the range of low pressure, ie from the aggregate module 15 to the tower 10 as described above.
  • Line G highlights the line of 80% relative humidity.
  • An integrated dehumidification heat pump system is the moisture reduction of the outside air and their simultaneous heating with the overall effect that after cooling the outside air in the tower 10, the dew point is not reached or can not be achieved, so that condensation in the tower 10 and in the nacelle. 1 1 is avoided.
  • Optional dehumidification heat pump changeover with an additional condenser to circulating air for emergency heating, especially in winter operation and / or when the wind turbine is shut down.
  • intermediate decks offer a good opportunity to maintain or increase the dynamics of the supply air flow by selectively increasing the flow rate of the supply air at a preferably centrically arranged device, which increases the velocity of the supply air flow, such as a nozzle or a diffuser, and a directed flow Reproduced with high induction behavior above each sub-deck.
  • a preferably centrically arranged device which increases the velocity of the supply air flow, such as a nozzle or a diffuser, and a directed flow Reproduced with high induction behavior above each sub-deck.
  • This arrangement can be repeated for each intermediate deck, wherein the speed increasing means is designed such that the beam length reaches the height of the respective next intermediate deck and is picked up and continued there by the next speed increasing unit.
  • the intermediate deck according to FIGS. 30 and 31 has gaps at its side edges to the tower wall or openings are provided in the intermediate deck for carrying out an elevator cabin or other facilities, mechanical additional equipment such as ventilators 80, 81, 82 are required in FIG to increase the dynamic speed of the supply air flow ZL, ZL ', ZL ", ZL'", since the introduced via the outside air fan air quantity penetrates all openings due to the large Druckverhal-, resulting in an uncontrolled flow behavior in the tower 10 and the nacelle 1 1 develop can.
  • FIG. 31 shows the generation of a propulsion jet formed from the primary air and secondary air flows formed by induction and bypass flows occurring in the region of the intermediate deck above the aggregate module 15 at the edge regions of the intermediate deck, corresponding to the arrows indicated in FIG. 31.
  • the fans 80, 81, 82 which generate the flow in the central region of the tower 10 again, with a slightly elevated, suitable amount of air, for example, + 10%, interpreted as compared to the supply air, so that by overpressure above the respective intermediate deck and negative pressure below the respective intermediate deck a small amount of air flows through the bypasses and thus prevents uncontrolled air flows from the over-pressure behavior of the outdoor fan 25 arise.
  • the mechanical air conveyors in the form of additional fans 80, 81, 82 are designed with an extremely low static pressure, because the dismiss Kunststoffventi- vator 25 generates a significant excess pressure, which can only flow in the nacelle 11 after all the way through the tower 10 and finally Only there loses through leaks and pressure flaps as exhaust air FL.
  • the tower 10 is to be regarded as hermetically closed, so that here the excess pressure is maintained until entry into the nacelle 1 1.
  • FIG. 32 shows the optimized air treatment system 6 for the wind energy installation shown in FIG. 30 in conjunction with the conventional air treatment or desalination apparatus 2 for the pre-dehumidification and desalination of the outside air AL.
  • the arrangement of a high-performance filter as well as a heat exchanger or an additional heating device in the optimal air treatment device 5 can also be displaced or additionally arranged according to FIG. 34 in the region of a nozzle with fan 80 above the aggregate module 15 with the high-efficiency filter 59 and the heat exchanger 8.
  • the solution according to the invention has been described above using the example of an offshore wind power plant with the prevailing in seawater climatic conditions of a moist and salty outside air at seasonal very cold or very warm outside air temperatures. This results in the requirements of dehumidifying and desalination of the outside air and providing a dehumidified and desalinated supply air in the area of the unit module 15, inside the tower 10 and in the nacelle 11 to prevent corrosion and ensure the discharge of the in the aggregate module accumulating heat loads.
  • the solution according to the invention is also applicable to other environmental conditions, for example to an environment with sandy, dusty or otherwise heavily contaminated outside air. Even under such conditions, the use of a heat pump and filter device for conditioning the injected into the tower interior air and heat dissipation of radiated from the electrical and electronic units in the unit module heat is of importance.
  • dehumidification and the associated safety against condensation is also significant in land-based wind turbines, as wind turbines have electrical and electronic equipment that is sensitive to excessive humidity levels at which they are subject to increased corrosion , as well as react to impermissibly high temperatures, which can lead to the destruction of the electrical and electronic devices see.
  • not all devices must be arranged directly in the tower in such wind power plants, but can also be provided in containers or buildings next to the tower of the wind energy plant. Even at such outbuildings or containers, the dehumidification of the outside air or the prevention of condensation and optionally the heat dissipation of the electrical and electronic units of considerable importance.
  • the risk of corrosion depends essentially on the climatic conditions at the location of a wind power plant.
  • the measures described above are used to maintain the temperature and humidity values of the air inside the wind energy plant, which are outside the critical humidity.
  • the measures eliminating or at least minimizing the risk of corrosion, however, it should be noted that the electrical and electronic units arranged in the tower and the nacelle of the wind power plant are sufficiently cooled for safe, permanent operation. In certain regions, the case may occur that, although the air is adequately desalinated and dehumidified, the supply air flow discharged into the tower and / or into the nacelle of the wind energy installation has a temperature height that is too high for cooling the units is or is not completely sufficient for cooling. In these cases, the use of an optimized with respect to the cooling air treatment device by way of Zu Kunststoffstromes in the tower of the wind power plant or within the nacelle of a wind power plant according to the below-described Fig. 39 to 45 is advantageous.
  • Fig. 39 shows an air treatment system with a combination of an improved air treatment device 4 with a conventional air treatment or desalination unit 2 "according to FIG. 13 below the dotted line and a plate heat exchanger 91 with separate air flow guide in conjunction with an additional fan 92 above the dotted line
  • the other, from the supply air flow ZL-ZL 'hermetically separated air flow leads from the outside air AL via the additional fan 92 to the exhaust air FL.
  • the supply air flow ZL-ZL 'via the plate heat exchanger 91 becomes free, indirect cooling in which the outside air flow is conducted from the outside air connection AL to the outgoing air connection FL via the plate heat exchanger 91 and thereby indirectly cools the supply air flow ZL-ZL '
  • the two air flows guided through the plate heat exchanger 91 are hermetically separated, so that a contamination of the supply air flow ZL-ZL 'is excluded with salty and humid air.
  • the maximum temperature can reach the value of the outside temperature and with respect to the humidity can not exceed the value of 65% relative humidity.
  • the targeted dehumidification by means of the combination of improved air treatment device with conventional air treatment or desalination apparatus according to FIG. 13 ensures that the dew point is never reached at any time and at any location within the tower 10, so that a secure corrosion protection even under consideration linear increase in corrosion rate at humidity levels greater than 65% relative humidity is achieved.
  • the air treatment system illustrated in FIG. 39 with a combination of improved air treatment device 4 with a conventional air treatment or desalination device 2 "in conjunction with a plate heat exchanger 91 for indirect free cooling of the supply air ZL 'discharged into the tower 10 or into the aggregate module 15 serves in FIG primarily the cooling of the supply air ZL 'for sufficient cooling or heating of the electrical and electronic units arranged in the tower 10 or in the nacelle 11.
  • the fans 25, 92 arranged in the air treatment system according to FIG. 39 are preferably equipped with controllable drives to ensure a constant temperature with targeted temperature increase and constant maintenance, so that via the volume flow the cooling or the use of the waste heat for tower heating inwinter months can be regulated from 0 to 100%.
  • FIG. 40 shows the air treatment system according to FIG. 39 with an additional mechanical cooling device consisting of a compressor 930, an evaporator or radiator 931 and a condenser 932.
  • This modified air treatment system for a wind power plant is preferably used for installation in climatic zones, the higher ones Outdoor temperatures that are insufficient for a free, indirect cooling.
  • the free, indirect cooling is used in a first sequence and depending on the season or demand, the mechanical cooling system 930, 931, 932 in a second sequence targeted or regulated switched.
  • the fans 25, 92 are equipped with controllable drives for generating variable volumetric flows as a function of the temperature.
  • Fig. 41 shows a schematic representation of a device that can be used in sub-areas of the wind power plant 1 for additional, or complementary or independent cooling of aggregates, such as the transmission and the generator in the nacelle 11 of the wind energy plant 1 ,
  • the device for additional cooling of units comprises a plate heat exchanger 94 with separate, but in heat-exchanging connection air flow guides an outside air flow, which leads from an outside air connection AL to a continuous air connection FL via a first fan 95, and a recirculation air flow from a supply air connection ZL 'leads to a supply air connection ZL "via a second fan 96.
  • the first fan 95 conveys outside air AL via the plate heat exchanger 94 to the exhaust air FL and thereby cools the hermetically separated recirculating air flow ZL'-ZL" to use the free, indirect cooling the second fan 96 is conveyed.
  • the fans 95 and 96 are equipped with controllable drives to achieve variable volume flows as a function of the temperature.
  • the device illustrated in FIG. 42 differs from the device according to FIG. 41 in the arrangement of an additional mechanical cooling with a compressor 970, an evaporator 971 and a condenser 972.
  • This device is used to set up the wind power plant in climatic zones, have the higher outside temperatures, which are not sufficient for a free, indirect cooling, so that the mechanical refrigeration system 970, 971, 972 can be switched on for additional mechanical cooling.
  • the free cooling is used in the first sequence and the mechanical cooling system 970, 971, 972 is activated in a targeted or regulated manner in a second sequence depending on the season or demand.
  • the fans 95 and 96 are equipped with controllable drives in order to achieve variable volume flows as a function of the temperature.
  • FIG. 43 shows a schematic representation of a wind power plant 1 with a tower 10 and a nacelle 11, in which the air treatment systems LBS and E are arranged with supplementary cooling devices or cooling devices according to FIGS. 39 to 42.
  • the modified air treatment system LBS according to FIG. 39 or 40 is used in the lower part of the tower 10, which supplies a supply air flow ZL 'to the inside of the tower cooled down as required and regulated
  • a device E according to FIGS. 41 or 42 is provided in the nacelle 1 1, which cools the air within the nacelle 1 1 by using an additional outside air flow from the outside air connection AL to the exhaust air connection FL.
  • the arrangement according to FIG. 43 is only to be understood as an example.
  • FIG. 44 shows, on a temperature example for the area of the German North Sea, the effect of the modified air treatment systems in the tower 10 and in the nacelle 11 of the wind power plant 1.
  • the modified air treatment system LBS in the lower part of the tower 10 draws in outside air with a flow velocity of 10,000 m 3 / h at a temperature of 20 0 C and a relative humidity of 90%.
  • the combination of an improved air treatment device with a conventional air preparation or desalination apparatus according to FIG. 13 supplies a supply air flow ZL at a flow rate of 5,000 m 3 / h at a temperature of 40 ° C.
  • the supply air ZL 'cooled down by means of the plate heat exchanger is delivered to the unit module or the interior of the tower 10 at a flow rate of 5,000 m 3 / h at a temperature of 27.4 ° C. and a relative air humidity of 60%.
  • the cooling of the nacelle 11 is favorably influenced.
  • Fig. 45 shows a schematic representation of a method for increasing the cooling effect through the tower walls.
  • the introduced, dehumidified and desalinated outside air absorbs this heat and flows up into the nacelle 11
  • the nacelle 1 1 are again aggregates such as transmission and generator, which also give off heat or require cooling. For this reason, it is necessary that the upwardly flowing and already heated air is sufficiently cooled in order to have in the nacelle 1 1 on the necessary cooling effect for the units set up there.
  • the big steel mass of the Turmes 10 offers an excellent opportunity for this, but the cooling effect is low when the upflowing current reaches the nacelle 11 by spinning.
  • a speed-increasing device for example an air-conveying device in the form of a fan and a nozzle, is arranged at the starting point S according to FIG. 45.
  • the nozzle may have any geometric shape, for example a round shape or a flat-jet shape. Also, depending on the tower height and / or the tower diameter, one or more further nozzles or devices can be arranged.
  • the device is arranged so that the air is driven at high speed obliquely upward, sharply up the tower wall.
  • the blown-in air stream virtually sticks to the tower wall and generates a rotary movement (vortex flow) throughout the tower 10, which tears open the air layers and air layers and ensures that this movement results in better contact with the tower wall and thus the Cooling effect is significantly improved.
  • the thermal boundary layers are torn open and the heat transfer is substantially improved, that is to say a marked improvement in the heat transfer coefficient is achieved, since the intensity of the heat transfer at the boundary surface becomes considerably stronger.
  • Air treatment or desalination device Air treatment or desalination device

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Combustion & Propulsion (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Power Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Central Air Conditioning (AREA)
  • Wind Motors (AREA)

Abstract

Procédé et dispositif de gestion de l'air dans des installations d'énergie éolienne offshore comportant une tour dont l'extrémité supérieure présente une gondole (11) possédant un générateur et au moins une pale de rotor (12) et dont l'espace intérieur contient des groupes (16) électriques et électroniques produisant de la chaleur, tels que des systèmes de commutation, des dispositifs de couplage, des transformateurs, des convertisseurs de fréquence, par exemple, et situés dans un module commun (15) de la tour (10), qui présente au moins une ouverture d'entrée d'air et des ouvertures de sortie d'air (3).L'air extérieur AL aspiré depuis l'environnement de la tour (10) par l'ouverture d'entrée d'air, est conduit par l'intermédiaire d'un premier trajet d'écoulement AL'-ZL d'un système de gestion d'air (6) comportant un dispositif de gestion d'air (5) à trajets d'écoulement AL'-ZL, UL séparés. Le deuxième trajet d'écoulement UL en échange de chaleur avec le premier trajet d'écoulement AL'-ZL passe par un circuit fermé à travers le module commun (15) et transfère l'énergie thermique absorbée par le transfert de chaleur des groupes électriques et électroniques (16) au premier trajet d'écoulement AL'-ZL par l'intermédiaire du dispositif de gestion d'air (5), l'air réchauffé ZL' ' sortant du module commun (15) étant transféré avec une surpression à l'espace intérieur (100) de la tour (10) et de la gondole (11).
EP09781552A 2008-08-06 2009-08-06 Procédé et dispositif de gestion de l'air dans des installations d'énergie éolienne Withdrawn EP2326836A2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102008041054 2008-08-06
DE102008053814A DE102008053814A1 (de) 2008-08-06 2008-10-23 Verfahren und Vorrichtung zur Luftbehandlung in Wind-Energieanlagen
PCT/EP2009/060199 WO2010015674A2 (fr) 2008-08-06 2009-08-06 Procédé et dispositif de gestion de l'air dans des installations d'énergie éolienne

Publications (1)

Publication Number Publication Date
EP2326836A2 true EP2326836A2 (fr) 2011-06-01

Family

ID=41501421

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09781552A Withdrawn EP2326836A2 (fr) 2008-08-06 2009-08-06 Procédé et dispositif de gestion de l'air dans des installations d'énergie éolienne

Country Status (3)

Country Link
EP (1) EP2326836A2 (fr)
DE (1) DE102008053814A1 (fr)
WO (1) WO2010015674A2 (fr)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100277869A1 (en) * 2009-09-24 2010-11-04 General Electric Company Systems, Methods, and Apparatus for Cooling a Power Conversion System
EP2466128B2 (fr) * 2010-12-20 2017-06-28 Siemens Aktiengesellschaft Éolienne et procédé de commande d'une éolienne et système de climatisation
DE102011103311A1 (de) * 2011-05-26 2012-11-29 Aerodyn Engineering Gmbh Windenergieanlage mit geschlossenem Kühlkreislauf
EP2568169B2 (fr) 2011-09-09 2021-11-10 Siemens Gamesa Renewable Energy Deutschland GmbH Éolienne dotée d'un système de climatisation en forme de tour utilisant de l'air extérieur
EP2639450B1 (fr) * 2012-03-13 2016-05-18 ALSTOM Renewables Technologies Wind B.V. Système de conditionnement d'air pour éolienne et procédé de ventilation et de mise en pression d'une éolienne
IN2012DE00735A (fr) * 2012-03-14 2015-08-21 Gamesa Innovation & Tech Sl
DE102012212619A1 (de) * 2012-07-18 2014-01-23 Mahle International Gmbh Frischluftversorgungseinrichtung sowie Verfahren zur Frischluftversorgung einer Off-Shore-Anlage
DK2808543T3 (en) * 2013-05-28 2017-12-18 Siemens Ag dehumidification
JP6356500B2 (ja) * 2014-06-19 2018-07-11 株式会社日立製作所 風力発電装置
DK201500002U3 (da) * 2015-01-12 2016-04-25 Cotes As Afsalter til offshore-vindmølle
DE102016213659A1 (de) * 2016-07-26 2018-02-01 Robert Bosch Gmbh Lüftungseinrichtung und Verfahren zum Betrieb einer Lüftungseinrichtung
CN109715938B (zh) * 2016-09-09 2021-08-03 西门子歌美飒可再生能源公司 用于风力涡轮机的过渡件
CN108843525B (zh) * 2018-06-28 2020-07-28 十堰善新新能源科技有限公司 一种风力发电机组内壁散热装置
US10954922B2 (en) * 2019-06-10 2021-03-23 General Electric Company System and method for cooling a tower of a wind turbine
CN112780509B (zh) * 2019-11-01 2023-07-28 新疆金风科技股份有限公司 空气冷却系统、风力发电机组及其冷却方法
CN113982867B (zh) * 2021-10-29 2023-03-17 中国船舶重工集团海装风电股份有限公司 一种海上风力发电机组塔底有害气体导出装置及方法

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1038103A1 (fr) * 1997-12-08 2000-09-27 Siemens Aktiengesellschaft Eolienne et procede de refroidissement d'un generateur d'une eolienne
DE10139556A1 (de) * 2001-08-10 2003-02-27 Aloys Wobben Einrichtung zur Entfeuchtung eines gasförmigen Mediums und Windenergieanlage mit einer solchen Einrichtung
DE102004061391B4 (de) * 2004-12-21 2010-11-11 Repower Systems Ag Temperaturregelung in einer Windenergieanlage
DE102005029463B4 (de) * 2005-06-24 2015-10-29 Senvion Gmbh Turmentfeuchtung einer Windenergieanlage

Also Published As

Publication number Publication date
WO2010015674A2 (fr) 2010-02-11
WO2010015674A3 (fr) 2010-06-03
DE102008053814A1 (de) 2010-02-11

Similar Documents

Publication Publication Date Title
EP2326836A2 (fr) Procédé et dispositif de gestion de l'air dans des installations d'énergie éolienne
DE102004046700B4 (de) Windenergieanlage mit einer Generatorkühlung
EP1926400B1 (fr) Procede et dispositif pour creer une atmosphere conditionnee
EP1736665B1 (fr) Déshumidification de l'intérieur de la tour d'une éolienne
DE102009056968B3 (de) System und Vorrichtungen für Luftbehandlung aufdachs eines Fahrzeugs
WO2011091863A1 (fr) Procédé et dispositif pour la déshumidification de l'air ambiant dans le domaine off-shore
EP1407966B1 (fr) Condenseur
DE10350541A1 (de) Klimatisierungssystem und Verfahren zur Aufbereitung von Luft zur Klimatisierung eines Raumes
EP1821042A2 (fr) Dispositif de déshumidification
CH654098A5 (de) Verfahren zum regulieren der kuehlung eines luftgekuehlten dampfkondensators und dampfkondensator.
EP3048296A1 (fr) Procede de degivrage d'une pale de rotor d'une eolienne
DE2630667A1 (de) Klima-dachgeraet
DE102011013856A1 (de) Vorrichtung zur veränderlichen Anströmung eines Wärmetauschermoduls
EP2418430B1 (fr) Dispositif de climatisation et procédé de conditionnement d'un flux d'air
DE60204993T2 (de) Frischlufteinlassvorrichtung eines Luftfahrzeuges
DE102011054257B4 (de) Klimagerät
EP2546595A1 (fr) Dispositif et procédé de refroidissement
EP1527914A2 (fr) Système pour tempérer l'intérieur d'un véhicule et procédé pour sécher un évaporateur d'air conditionné prévu dans un tel système
DE102004049621A1 (de) Klimagerät
WO2019086069A1 (fr) Aérogénérateur avec collecteur de co2 et procédé de commande ou de fonctionnement de collecteur de co2 d'aérogénérateur
EP1348911B1 (fr) Dispositif de climatisation d'air pour la commande du chauffage et de l'humidification dans une enceinte fermée
EP3258184A1 (fr) Dispositif pour un batiment, en particulier une piscine couverte, destine a echanger l'humidite et la chaleur
DE4325945C2 (de) Klimakühlturm
EP2913599B1 (fr) Dispositif de climatisation
EP2974894B1 (fr) Procédé de fonctionnement d'une climatisation d'un véhicule automobile

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20110307

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO SE SI SK SM TR

AX Request for extension of the european patent

Extension state: AL BA RS

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RIC1 Information provided on ipc code assigned before grant

Ipc: F03D 11/00 20060101AFI20121218BHEP

Ipc: F03G 6/04 20060101ALI20121218BHEP

Ipc: F04D 29/58 20060101ALI20121218BHEP

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20130601