DE102008053814A1 - Method and device for air treatment in wind power plants - Google Patents

Abstract

Method and apparatus for air treatment in offshore wind energy plants with a tower 10, at the upper end of a nacelle 11 with a generator and at least one rotor blade 12 and in the interior heat-dissipating electrical and electronic units 16 such as switchgear, switching devices, transformers, frequency converters and The like are arranged in an aggregate module 15 of the tower 10 and having at least one air inlet opening and air outlet openings 3. Outside air AL drawn in from the vicinity of the tower 10 via the air inlet opening is guided via a first flow path AL'-ZL of an air treatment system 6 with an air treatment device 5 with separate flow paths AL'-ZL, UL. The second flow path UL, which is in heat-exchanging connection with the first flow path AL'-ZL, is guided through the aggregate module 15 in a closed circuit and supplies the heat energy absorbed by the heat emission of the electrical and electronic units 16 via the air treatment device 5 to the first flow path AL '-ZL, from which, with the exclusion of the unit module 15 heated supply air ZL "with excess pressure to the interior 100 of the tower 10 and the nacelle 11 is discharged.

Description

The The invention relates to a method and an apparatus for air treatment in wind energy plants, especially in offshore wind power plants, according to the preamble the claims 1 and 21 to 23.

Wind turbines or correct wind energy systems and in particular offshore wind energy systems exist according to the schematic diagram in 1 from a tower founded in the seabed 10 at the top of which is a gondola 11 is arranged, in which there is a generator, via a drive shaft and a transmission with three rotor blades in the example shown 12 is connected, the angle of attack are generally adjustable to optimize the wind drive. The electrical power output by the generator is by means of electrical and electronic components and units 16 such as switchgear, switching devices, control and regulating devices, transformers, frequency converters, etc. processed and transmitted via cable to the mainland. The in an aggregate module 15 of the tower 10 arranged electrical and electronic units 16 control and regulate also the operation of the generator, employment of the rotor blades etc.

For cooling the heat-emitting electrical and electronic units 16 Outside air is AL over a generally below the aggregate module 15 arranged air inlet opening 14 , For example, an opening in an access door in the tower 10 , from an air handling unit 2 whose components are in 2 are shown schematically and described below, aspirated, cleaned and with positive pressure as supply air ZL to the interior of the tower 10 delivered so that the introduced and largely purified supply air flow ZL the aggregate module 15 flows through, from the electrical and electronic components and aggregates 16 emitted radiating heat and via outflow 13 in the gondola 11 is discharged as exhaust FL to the environment. Due to the overpressure in the interior of the tower 10 Prevents leaks over saline sea air in the interior of the tower 10 and the gondola 11 penetrates and accelerates corrosion processes. The partially desalinated air flows freely through the aggregate module 15 and the tower 10 to the gondola 11 and can escape there by leaks overpressure.

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 , In a first stage, the air treatment unit 2 a first droplet separator 21 as the main separator for coarse pre-separation of rain, spray etc. In a second stage are designed as an aerosol filter coalescence 22 . 23 provided, bind the aerosols and form larger drops. In a third stage, a second droplet follows 24 as Nachabscheider, which intercepts and separates the previously formed drops. The required air flow is by means of an outside air or overpressure fan 25 generated.

• 1. mit einem gereinigten Luftstrom wird die Oberflächenwärme der Komponenten im Turm 10 und in der Gondel 11 abgeführt;
• 2. die eingebrachte Seeluft (Außenluft) wird von den in der Luft enthaltenen Salzaerosolen zum Schutz der innerhalb des Turmes 10 der Offshore Wind-Energieanlage 1 im Aggregatemodul 15 angeordneten elektrischen und elektronischen Aggregate 16 vor Korrosion gereinigt;
• 3. durch Überdruck der in den Turm 10 und die Gondel 11 eingebrachten und größtenteils gereinigten Zuluft ZL wird verhindert, dass Seeluft mit einem hohen Salzgehalt eindringt. Dabei wird der Zuluft- und Überdruckventilator 45 in Abhängigkeit von der äußeren Windgeschwindigkeit druckabhängig betrieben, wobei ein Überdruck von ca. 2000 Pa erzeugt werden kann, so dass selbst bei Starkwind, d. h. bei Windgeschwindigkeiten bis 56 m/sec, die eingebrachte, größtenteils gereinigte Zuluft ZL über im wesentlichen in der Gondel 11 vorhandene Undichtigkeiten 3 und durch entsprechende Überdruckklappen entweichen, d. h. nach außen abströmen kann, während das Eindringen von ungereinigter, salzhaltiger Seeluft selbst bei Starkwind in das Innere des Turmes 10 und der Gondel 11 durch den erzeugten Überdruck verhindert wird.

That in the offshore wind energy plant 1 provided air conditioning system according to 2 fulfills the following tasks:

• 1. with a purified air flow, the surface heat of the components in the tower 10 and in the gondola 11 dissipated;
• 2. the introduced sea air (outside air) is protected by the salzaerosols contained in the air to protect the inside of the tower 10 the offshore wind energy plant 1 in the aggregate module 15 arranged electrical and electronic units 16 cleaned from corrosion;
• 3. by overpressure into the tower 10 and the gondola 11 introduced and largely purified supply air ZL prevents sea air with a high salt content penetrates. This is the supply and overpressure fan 45 operated depending on the external wind speed pressure dependent, with an overpressure of about 2000 Pa can be generated so that even in strong winds, ie wind speeds up to 56 m / sec, the introduced, largely purified supply air ZL over substantially in the nacelle 11 existing leaks 3 and escape through appropriate pressure flaps, ie, can flow to the outside, while the ingress of uncleaned, salty sea air even in strong winds in the interior of the tower 10 and the gondola 11 is prevented by the generated pressure.

A disadvantage of this conventional air treatment in offshore wind energy plants 1 is that the treatment of the sea or outdoor air AL by desalination, although a significant reduction in the salt content achieved, but is a permanent residual salt in the tower 10 registered, in particular in the form of dissolved in the outside air aerosols from the drop and Koaleszenzabscheidern the air treatment unit 2 can not be filtered out. Thus, the setpoint of the residual salt content of the air of about 0.005 mg / m ³ is exceeded by 100 times, so that the electrical and electronic units 16 be contaminated despite the air treatment and after a relatively short time a significant corrosion of the electrical and electronic units 16 takes place.

Salt has different states of aggregation depending on the moisture content. At egg With a moisture content of> approx. 70%, salt is in the liquid state of aggregation. With 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.

Of the The present invention is based on the object, a Method and device for air treatment in wind power plants and Specify in particular in offshore wind energy plants, the one Elimination or reduction of salt and moisture content and so that the risk of condensation (dew point below) the to the aggregate module and into the tower or the gondola with overpressure ensure that the air is exhausted.

These Task is performed by a procedure with the characteristics of Claim 1 and devices with the features of claims 21 to 23 solved.

The Ensure solutions according to the invention an elimination or at least a significant reduction of the Salt and moisture content and thus reduce the risk of Condensation due to dew point undershooting of one to the aggregate module and in the tower or the nacelle of an outside air fan with overpressure outside or supply air volume flow and thus the risk of corrosion the arranged in the aggregate module electrical and electronic Aggregates as well as the inner wall and the devices in the tower and in the gondola.

These simple air treatment device assumes that by heating the outside air a relative humidity of 40% which crystallized into particles Salzaerosols deposited in a high-performance filter as salt particles can be. In order to is indeed 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 gondola, however, can not be climatic under all Conditions and year round be sure that the air flow in the unit module and maintained in the interior of the tower and the gondola in the way is that on the one hand the electrical and electronic Aggregates emitted heat is sufficiently safe dissipated and on the other hand, a risk of corrosion inside the tower and the Gondola can be excluded.

Furthermore is taken into account, that the wind power plant during many annual hours is not in operation, for example, in storm, light wind, Incidents and for maintenance purposes. To be also during This year's maximum security regarding overpressure, salt-free, Temperature maintenance, humidity and condensation prevention delivered to the aggregate module and in the tower and the nacelle To ensure supply air an emergency operation is required, which is insufficiently guaranteed with this method can be.

One improved air treatment system is therefore characterized that over the air inlet opening moist and salty outside air drawn in from around the tower cooled in an air treatment device while the absolute Humidity of the outside air is lowered, that the cooled and dehumidified outside air is heated until a predetermined relative humidity of the outside air is reached, in the those contained in the outside air Salzaerosols are at least partially crystallized, that crystallized Salzaerosole and in the outside air contained salt particles are deposited and that the dehumidified and desalinated outside air as supply air to the interior of the tower and / or to the unit module is delivered.

By the cooling off the humid and salty outside air at the same time Reduction of the absolute moisture content of the outside air and the subsequent one Afterheating is a humidity value of the treated outside air of less than or equal to 40% relative humidity, so that still in the outside air Salzaerosole contained crystallized and deposited can. After dehumidification and desalination of the outside air, the supply air flows freely and without special air distribution systems in or through the aggregate module and through the upper part of the tower to the gondola. This ensures that the dehumidified and desalinated supply air even with total re-cooling to the temperature value the outside air due to cooling on the way from the aggregate module to the nacelle at no point the low Level of dew point, d. H. a relative humidity of 100%, can reach what the risk of condensation throughout the wind energy plant and thus significantly reduces the risk of corrosion.

A further optimized air treatment system is characterized in that the moist and saline outside air sucked 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 recirculating air flow communicating in heat exchange with the outside air a closed circuit through the Aggregate module is guided and emits the thermal energy absorbed by the electrical and electronic units heat energy to the outside air, is discharged from the heated under exclusion of the aggregate module supply air with overpressure to the interior of the tower and the nacelle.

The optimized air treatment system ensures a powerful Cooling the surface heat release the electrical and electronic units and a controlled Temperature maintenance in the tower to the nacelle by controlled heat transfer with power from the waste heat the electrical and electronic units. As a result of the hermetic separate leadership two air streams is achieved that the still contaminated with salt outside air no longer flows freely through the aggregate module and thus the electrical and electronic aggregates can not contaminate.

Preferably are the volume flow of the outside air and / or the circulating air independently generated from each other and to adjust the heat transfer in the aggregate module and / or the temperature or humidity of the supply air controlled and regulated.

The Control and regulation of the circulated Recirculation allows a continuous adjustment of the required circulating air and thus a circulation suitable air quantities. By variable air volumes of both the outside air to the supply air as well as the circulating air depending on parameters such as Outside air temperature, Humidity and salinity of the outside air as well as in dependence from the required in aggregate module cooling power and emergency heating at Standstill of the wind energy plant can significantly reduce the air handling to be influenced. In particular, with a setting variable Air volumes of fresh air supply air or circulating air is a significant factor influencing energy consumption or the energy costs, since a reduction of the outside air supply air and circulating air volumes in lowered operation in appropriate weather conditions and at lower heat loads Saves energy costs in the aggregate module.

In an embodiment contains the air treatment device an air treatment device with heat recovery, through the hermetically separated flow paths the outside air supply air flow and the circulating air flow are performed and one in the flow direction the outside air supply air flow Before and / or after the air treatment unit with heat recovery arranged condenser or Reheat Registry a dehumidification heat pump, the one evaporator, the at least one condenser or reheat register, and a compressor.

Independent of an arrangement of the condenser of the dehumidification heat pump in the flow direction before or after the air treatment unit with heat recovery, the dehumidification purpose, d. h., the moisture reduction met in the same way.

The Arrangement of the condenser of the dehumidification heat pump in the flow direction in front of the air handling unit with heat recovery with an immediate reheating after cooling in the Evaporator of the dehumidification heat pump Although reduces the cooling effect the circulating air flow in the air treatment unit with heat recovery, since the outside air supply air already heated in the condenser was, what would be technically disadvantageous, the functionality the dehumidification heat pump but do not affect would.

Becomes the outside air supply air flow immediately after leaving the air treatment unit with heat recovery, d. H. according to the heat released from the circulating air, with the energy from the Dehumidification process over The condenser or the reheat register additionally heated, so is an even more favorable, namely lower value of the relative humidity of the outside air supply air flow causes.

The Arrangement of the evaporator and condenser is not mandatory on Air inlet or air outlet of the plate heat exchanger required, but can also be anywhere within the duct system of the blown into the tower Zuluftstromes be provided.

alternative contains the dehumidification heat pump two capacitors or reheat registers, from which a first capacitor in the flow direction of the outside air supply air before the air handling unit with heat recovery and the second condenser in the flow direction of the outside air supply air flow after the air treatment device with heat recovery is arranged. By switching from the first capacitor to the second capacitor or by stepwise connection of the second Condenser to the first capacitor, the supply air flow continues heated.

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. Accordingly, the first condenser is preferably in the winter and the second condenser is preferably in the summer used. Depending on the requirements of both capacitors can be driven in Teillastbe operation, both capacitors are automatically controlled in mutual operation or variable partial loads.

Preferably the proportion of outdoor air supply air flow passed through the heat recovery air handling unit dependent on from a temperature and / or humidity control of the optimized air treatment system set.

By the setting of the outdoor air supply air flow passed through the heat recovery air handling unit can influence the energy exchange and thus the temperature and / or Moisture behavior of the air treatment device are taken.

In a further embodiment is in the circulating air flow path a capacitor arranged on the when heating demand in the unit module is switched.

By this embodiment can be used for heating 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, by the from the evaporator or cooler, Condenser or reheat register and compressor formed dehumidification heat pump in the outside air supply air flow from the condenser of the dehumidification heat pump to the condenser be switched in the circulating air flow, so that the dehumidification heat pump in the outside air supply air flow AL / ZL the supply air of the recirculated air delivered to the unit module second flow path heated. The energy for This heating operation is thereby operated by others in the network Offshore wind energy plants delivered.

By a bypass from the supply air flow to the circulating air flow between the from Evaporator or cooler, Condenser or reheat register, compressor and high-performance filter formed dehumidifying heat pump in the circulating air flow for overpressure maintenance in the circulating air flow is achieved that by the aggregate module flowing Circulating air is not due to currents from other areas of the wind turbine with saline air contaminated, the required amount of bypass air very is small, the moisture content of the circulating air is not significantly affected and prevents negative flows from the area of the Tower of wind turbine or air intake in the aggregate module can penetrate.

Preferably the discharged from the air treatment device to the tower interior Supply air flow over a heat exchange device to be led, the waste heat the electrical and electronic units recorded heat energy to the supply air flow in dependence from the air temperature in the interior of the tower and the nacelle, wherein the supply air at least in the section between the air treatment device and the entry into the interior of the tower in a supply air duct guided becomes.

The Effect and positive consequences of the heat exchange device exist in that to avoid condensation within the tower and the gondola is overflowing the heat exchange device warmed up so far is, d. H. a temperature increase causes even by the cooling effect of the tower walls and a drop in the temperature of the supply air in the tower and the Gondola the dew point is not reached.

The Air treatment device not only causes dehumidification and Desalination of the outside air discharged by the air treatment unit, but takes over also the cooling the aggregate module by a targeted air extraction from the individual Floors or platforms of the unit module via circulating air exhaust ducts and a targeted air supply over Forced-air inlet ducts into the individual floors or platforms of the aggregate module.

In a further embodiment if the supply air discharged by the air treatment device is additionally dehumidified, with the energy gained from the dehumidification process before the Dispensing to the interior of the tower heated and at high speed and preferably in the center of the tower diameter in the interior blown in the tower.

Farther can the over the air inlet opening Wet and salty outdoor air drawn in from around the tower Droplet separator for coarse pre-separation of rain, spray passed become.

Preferably becomes the air treatment system according to the invention an air handling unit for desalination of the outside air and for generating an overpressure Downstream in the interior of the tower, preferably a first droplet separator for coarse pre-separation of rain, spray and the like, a Koaleszenzabscheider to Formation of larger drops, one second drop separator as Nachabscheider for interception and separation the previously formed droplets and the required air flow generating Fresh air or overpressure fan having.

A first device for air treatment in Wind power plants, in particular in offshore wind power plants, with a tower, at the upper end 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 converters and the like in one Aggregate module of the tower are arranged 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 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-crystallized Salzaerosole in the outside air or desalted and dehumidified outside air and delivery erw poor supply air via the unit module in the tower and in the nacelle.

These simple air treatment device makes it possible by heating the outside air to a relative humidity of 40% which crystallized into particles Salzaerosole in a high-performance filter as salt particles deposit. The associated significant reduction of the residual salt content and thus the risk of corrosion in the unit module as well as in the interior However, the tower and the gondola can not be climatic Conditions and year round make sure the air flow in the aggregate module and in the interior of the tower and the nacelle in the Way is maintained, so that on the one hand of the electrical and electronic units dissipated heat is dissipated with sufficient certainty and on the other a risk of corrosion inside the tower and the gondola can be excluded. Also, no emergency operation in storm, Low wind, accidents and too Maintenance possible.

A improved device for air treatment in wind power plants, especially in offshore wind energy plants, with a tower at whose the upper end of a gondola with a generator and at least one Rotor blade and in its interior heat-releasing electrical and electronic units such as switchgear, switching devices, Transformers, frequency converters and the like in an aggregate module of the tower are arranged and the at least one air inlet opening and an air outlet having, over 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 one from an evaporator to reduce the absolute moisture content the supplied outside air or the desalted in an upstream air treatment or desalination unit and dehumidified outside air, one Condenser or reheat coil for reheating the outside air to a relative humidity of less than or equal to 40% and one Compressor existing dehumidification heat pump, and with a high-performance filter for salt separation.

With the improved air treatment device is characterized by the cooling of the moist and salty outside air with simultaneous reduction of the absolute moisture content of Outside air and the subsequent one Reheating a humidity value of the treated outside air of less than or equal to 40% Relative humidity reached, so that still in the outside air salzaerosols crystallized and contained in a high performance filter can be separated. After dehumidification and desalination of the outside air, the supply air flows freely and without special air distribution systems in or through the aggregate module and through the upper part of the tower to the gondola. This ensures that the dehumidified and desalinated supply air even with total re-cooling to the temperature value the outside air due to cooling on the way from the aggregate module to the nacelle at no point the low Level of dew point, d. H. a relative humidity of 100%, can reach what the risk of condensation throughout Wind energy plant and thus the risk of corrosion significantly reduced. However, this is not an optimal energy solution and no targeted airflow in the aggregate module or in the tower interior possible.

One optimized air treatment system with a third, optimal device for air treatment in wind power plants, especially in offshore Wind energy plants, with a tower, at the top one Gondola with a generator and at least one rotor blade and in its interior heat dispensing 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 the at least an air inlet opening and an air outlet having, over 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, the first flow path the above sucked in the air inlet opening outside air to the interior of the tower except for the aggregate module discharged supply air leads and the second flow path in Recirculation mode, supply air to the unit module and exhaust air or return air sucked from the aggregate module.

Preferably contains the air treatment device with recuperative heat recovery system a plate heat exchanger, in the flow direction the first flow path after one with the air inlet connected air handling unit for desalination of the sucked outside air is arranged.

The optimized air treatment system ensures a powerful Cooling the surface heat release the electrical 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 electrical and electronic units and as a result of hermetic separate leadership two air streams, that the still contaminated with salt outside air is no longer free through the aggregate module flows and so that the electrical and electronic units do not contaminate can.

Preferably has the plate heat exchanger on the inlet side in the evaporator of the dehumidification heat pump cooled down outside air adjustable bypass flaps on which limit the number of plates set the plate heat exchanger can be in the outdoor air supply air flow used for energy exchange or passed by the energy exchange should, so over the adjustment of the bypass valves influences the energy exchange and thus on the temperature and / or humidity behavior of the air treatment device can be taken and the bypass valves in a temperature and Humidity control of the optimized air treatment system included can be.

In preferred embodiment is the outside air fan on the suction side, in the flow direction the outside air arranged to the supply air behind the air treatment device.

Basically the outside air fan both be arranged on the suction side and on the pressure side. The latter, for example, when the outside air fan, already Component of an existing, conventional air handling unit is and the air treatment device is retrofitted. Offers advantages however, the arrangement of the outside air fan on the suction side of the air treatment device, since he is here is located in dry, salt-free air, reducing the risk of corrosion the outside air fan is considerably reduced and therefore only low demands on the material quality of the outdoor fan are to be made. About that also allows the arrangement of the outside air fan on the suction side placements of the outside air fan, by the Aggregate module via all Between decks of the tower to the gondola as a site possible and are suitable.

By the arrangement of a supply air duct from the air treatment device to the separate from the aggregate module interior of the tower is in more consistent continuation the separation of the two flow paths through the plate heat exchanger the desalinated and dehumidified supply air in the supply air duct isolated from the recirculating air circulating in the unit module leads to the inside of the tower, so moisture or salt aerosols not contained in the supply air to the sensitive electrical and electronic devices in the unit module can reach.

Preferably is the supply air duct with a heat exchanger connected, of the arranged in the aggregate module electrical and electronic units absorbed heat energy in the interior leading the tower Supply air flow of the first flow path emits, with the heat exchanger delivered to the supply air heat energy dependent on controlled by the temperature in the interior of the tower and / or the nacelle and at least one the temperature in the interior of the tower and / or the gondola detecting temperature sensor connected to a control device is.

In analogous way, the recirculation in Zuluft- and exhaust air ducts from Plate heat exchanger led to and from the aggregate module, so that the circulating air flow over the air ducts in the individual Led floors of the unit module that is from the heat donated electrical and electronic units Heat removed and thus prevents residual moisture and residual salt content in the aggregate module can penetrate, wherein the air ducts also a targeted airflow and heat dissipation cause, so the heat donating electrical and electronic units regardless of their location effectively cooled become.

In Another embodiment of the invention is in the circulating air flow path another high-performance filter arranged, with the salt particles, which are not completely eliminated in the first treatment stage could, in addition be deposited.

Around the air resistance caused by the arrangement of the high-performance filter in the circulating air flow, and thus the energy consumption of the air treatment device lower, is the other high-performance filter in a bypass arranged with two jalousie flaps whose position is dependent determines the proportion of circulating air flow from a humidity measurement, which passes through the arranged in the bypass channel high-performance filter becomes.

In a preferred embodiment, the circulating air fan for infinitely variable delivery of recirculated air amounts to a regulated drive, creating a further possibility for temperature control is created. A reduction in the air volume of the circulating air flow, for example, has the consequence that less energy is transferred through the plate heat exchanger to the outside air supply air flow.

Either in the outside air supply air flow as well as in the circulating air stream can each be from an evaporator or Cooler, Condenser or reheat register and compressor existing dehumidification heat pump be arranged, wherein the circulating air dehumidification heat pump preferably in the exhaust air duct of the circulating air in the flow direction in front of the high-performance filter is arranged to circulating air in the salt particles and To eliminate aerosols, which may be leaking, while Assemblies or the like get into the aggregate module.

By a bypass for overpressure maintenance in Forced air-flow, which branches off from the supply air duct and to the circulating air flow path at the connection of the circulating air dehumidification heat pump is connected with the high-performance filter, it is achieved that flowing through the aggregate module Circulating air is not due to currents from other areas of the wind turbine contaminated with saline air is, with the required amount of bypass air is very small, the Moisture content of the circulating air is not appreciably influenced and prevents negative currents from the area of the tower of the wind turbine or the air inlet opening in penetrate the engine module so that the required amount of air only slightly is.

Farther can in the supply air flow path the air treatment device behind the plate heat exchanger and in front of the high power filter, an independent heater, preferably an electric heater, to be arranged.

By a bypass in the flow path the circulating air flow with controllable bypass flaps 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 independent mutually controllable bypass valves and a bypass line to Passing the Zuluftstromes on the high-performance filter, can be adjusted with a control device such a position that the airflows at cheap Humidity values either flow through the high-performance filters or over the Bypass lines are passed to the high-performance filters over.

In order to is ensured that salt crystals in the high-performance filters incurred and on the "impure" side stored at elevated humidity values do not disintegrate again to aerosols and on the "pure" side of the high-performance filter penetrate and over the increased Humidity in the aggregate module or in the tower or the nacelles are carried in.

The in the flow path the circulating air flow provided dehumidification heat pump, before the from the waste heat the electrical and electronic units in the aggregate module powered heating device is arranged and from an evaporator / cooler, compressor, and a first capacitor may be arranged around a in the outside air supply air second capacitor to be extended, the first capacitor assigned and operated together with this or mutually is. In this arrangement, an air treatment system consists of in the outside air supply air flow path arranged dehumidification heat pump from an evaporator / cooler, a compressor, a first condenser and a second condenser with reciprocal mode of operation.

The so designed dehumidification heat pump systems cause in the recirculation and outdoor air supply air an emergency heating, for example, frost protection of the air treatment device, or for additional Desalination and dehumidification at low temperatures and downtimes the wind turbine, since the dehumidification heat pump systems in the outside air supply air and circulating air flow through a very high efficiency at the lowest Power consumption provide a high heating power, whereas an electric heater at the same heat output more than fivefold Would cause power consumption. By the arrangement of the second condenser of the circulating air dehumidification heat pump in the outside air supply air flow can be according to requirement and heat requirement the energy output switched from 0 to 100% or regulated become. As the dehumidifying heat pump system in the outside air supply air flow also over two Has capacitors, can the heat energy ever as required in the direction of air before or after the plate heat exchanger and regulated from 0 to 100%.

Preferably, a jet nozzle for blowing a Zuluftstromes 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 specifically in the upper region of the tower and closer can be brought to the nacelle, wherein the air jet at high velocity on its flow path induces permanent air from all sides of the tower, so that air stratification and temperature stratification torn and secondary flows be avoided.

The preferably Centric arrangement of the jet nozzle avoids a distraction and leaning on the flow to the tower wall and thus the so-called Koander effect. For the introduction of air will a nozzle or diffuser shape chosen because while the static pressure losses are kept low.

On Intermediate decks of the tower arranged mechanical air handling equipment, especially fans, cause an increase in the dynamic speed the supply air flow, as the over the outside air fan introduced air volume due to the large pressure behavior openings in Temporary decks or elevator passages penetrate, causing an uncontrolled flow behavior in the tower as well as the gondola can develop.

In addition, the mechanical air handling equipment preferably with the waste heat of the arranged in the unit module, heat-emitting electrical and electronic units powered heating devices connected be what due to the cooling effect through the tower walls in connection with the long flow paths is advantageous. The temperatures throughout the tower can thereby across from a uniform central heating can be made more uniform and influence the temperature condensation behavior in the tower advantageous.

The inventive method and the inventive arrangement can also be used in wind power plants, the other loads are exposed, for example in desert or steppe regions with strong sand load of the sucked in outside air, what the use of special Filter in the air treatment unit or in the aftertreatment device required.

Based several embodiments shown in the drawing are intended to Essential features and advantageous embodiments of the invention and the advantages that can be achieved are explained in more detail. Show it:

1 a conventional prior art apparatus for air conditioning and air flow of an offshore wind energy plant;

2 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 energy plant;

3 a schematic representation of a simple air treatment system for aftertreatment and supplementary air treatment in an offshore wind energy plant;

4 a schematic representation of a portion of a tower of an offshore wind energy plant with a simple air treatment device 3 to reduce the salt content, dissipate the heat emitted by the electrical and electronic units and improve the moisture retention;

5 a schematic representation of part of a tower of an offshore wind energy plant with an improved air treatment system to reduce the salt content, dissipating the heat emitted by the electric and electronic units and improving the moisture retention;

6 a schematic representation of an improved air treatment device with a dehumidification heat pump and a high-performance filter of the improved air treatment system according to 5 ;

7 a Mollier-h, x diagram for humid air to explain the improved air treatment system according to 5 ;

8th and 9 two embodiments of a combination of an improved air treatment device according to 6 with a conventional air conditioner or desalination apparatus;

10 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 energy plant;

11 an air flow and system diagram of a first embodiment of an optimal air treatment device for the optimized air treatment system according to 10 ;

12 a longitudinal section through the housing of the first embodiment of the optimal air treatment device according to 11 ;

13 an air flow and system diagram of a second embodiment of an optimal air treatment device for the optimized air treatment system according to 10 ;

14 an air flow and system diagram of a third embodiment of an optimal air treatment device for the optimized air treatment system according to 10 ;

15 a longitudinal section through the housing of the third embodiment of the optimal air treatment device according to 14 ;

16 to 18 Luftführungs- and system schemes of other embodiments of an optimal air treatment device for the optimized air treatment system according to 10 ;

19 a Mollier-h, x-diagram for outside air and return air (circulating air) in summer and winter operation of an optimal air treatment device according to 18 ;

20 to 24 Luftführungs- and system schemes of other embodiments of an optimal air treatment device for the optimized air treatment system according to 10 ;

25 to 27 three embodiments of a combination of the optimal air treatment device according to 24 with the aggregates of a conventional air conditioner or desalination apparatus;

28 an offshore wind energy plant with an optimized air treatment system and a reheater or heat exchanger and a jet nozzle for blowing a supply air flow into the tower of the offshore wind energy plant at high speed;

29 a Mollier-h, x-diagram for explaining the effect of the optimized air treatment system with the optimal air treatment device;

30 an offshore wind power plant having a plurality of intermediate decks and speed increasing means configured as a nozzle or diffuser;

31 a detailed view of an intermediate deck with bypass flows and a nozzle with mechanical air conveyor;

32 a schematic representation of an air treatment system for an offshore wind energy plant in conjunction with a conventional air treatment or desalination apparatus;

33 an offshore wind energy plant with mechanical air handling equipment and heaters in multiple decks and

34 a detailed representation of an intermediate deck above an aggregate module with a nozzle with fan, a high-performance filter and a heat exchanger.

So far, in connection with the in 2 schematically illustrated conventional air treatment or desalination unit 2 those from the environment of an offshore wind energy plant 1 according to 1 sucked outside air AL coarsely desalinated and dehumidified and flows in uncontrolled, turbulent and free air flow as further moist and salzaerosols containing incoming air ZL on those in the aggregate module 15 of the tower 10 arranged electrical and electronic units 16 in the upper part of the tower 10 to the gondola 11 , There flows the tower 10 and the gondola 11 supplied supply air ZL by the outside air fan 25 in the air conditioner or desalination machine 2 according to 2 generated overpressure as exhaust FL. The residual salt content of the aggregate module 15 and the tower and the nacelle flowing through supply air ZL is a hundred times greater than the target value, so that the electrical and electronic units 16 and in the tower 10 or the gondola 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.

For the significant reduction of the residual salt content is according to the schematic representation of an offshore wind energy plant 1 according to 3 the over the air inlet opening 14 from the surroundings of the tower 10 sucked moist and salty outdoor air AL in the air treatment or desalination unit 2 according to 2 roughly desalinated and dehumidified. The roughly desalinated and dehumidified outdoor air AL is sent to a simple air treatment facility 3 are discharged, in which the outside air AL is heated and thereby crystallized to particles salt aerosols in the outside air AL are filtered out. The of the air treatment device 3 discharged supply air ZL flows through the aggregate module 15 , in free, unguided flow, takes away from the electrical and electronic aggregates 16 in the aggregate module 15 emitted radiant heat and exits the aggregate module 15 as heated supply air ZL 'in uncontrolled, spinning air flow in the upper part of the tower 10 and in the gondola 11 one. There, the supply air ZL 'flows through the outside air fan 25 in the air conditioner or desalination machine 2 according to 2 generated overpressure as exhaust air FL in the environment of the offshore wind energy plant 1 from.

4 shows in enlarged detail the area of the unit module 15 with the below the aggregate module 15 arranged conventional air treatment unit 2 and the simple air treatment device 3 , which is a heating device or an air heater 31 as well as a high performance filter 32 contains and that of the air conditioner or desalination equipment 2 treated outside air AL as supply air ZL to the unit module 15 emits. In the aggregate module 15 the supply air ZL flows on the electrical and electronic units 16 passing by, picks up the electrical and electronic aggregates 16 radiated heat energy and occurs above the aggregate module 15 as heated supply air ZL 'in the upper part of the tower 10 in which the heated supply air ZL as uncontrolled, spinning flow to the nacelle 11 rises.

The simple air treatment device 3 is based on the finding that salt aerosols crystallize to less than 40% 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, the salt aerosols crystallized to form particles can enter the heater 31 downstream high-performance filter 32 are deposited as salt particles.

Preferably, the heater is 31 with energy from the waste heat of the electrical and electronic units 16 in the aggregate module 15 fed, for example, by liquid cooling at least a portion of the electrical and electronic units 16 and recooling of the heat absorbed in the cooling liquid in a heater designed as an evaporator 31 ,

The above-described simple air treatment device 3 Although it ensures a significant reduction of the residual salt content and thus reduces the risk of corrosion in the unit module 15 as well as inside the tower 10 and in the gondola 11 Significantly, however, under all climatic conditions and year round can not ensure that the air flow in the aggregate module 15 and inside the tower 10 as well as the gondola 11 maintained in such a way that on the one hand of the electrical and electronic units 16 discharged heat is sufficiently safe and on the other hand, the risk of corrosion inside the tower 10 and the gondola 11 can be excluded.

In fact, during the winter months, the 40% moisture range of the Mollier-h, x-diagram is reached quickly and there is a sufficient temperature range that is equal to that of the electrical and electronic aggregates 16 of the aggregate module 15 discharged heat without the risk of overheating in the unit module 15 arises in the upper part of the tower 10 However, due to the low flow velocity in the large tower cross-section, incoming heated supply air ZL 'starts to spin and carries out uncontrolled flow movements which lead to secondary flows occurring in certain areas on the inner wall of the tower 10 fall to the dew point and lead to condensation of the supply air flow ZL '.

In addition, despite the lowering of the relative humidity of the supply air ZL to about 40%, it can not be ruled out that the residual moisture and the residual salt content in salt aerosols in the supply air ZL will lead to corrosion on the electrical and electronic units 16 in the aggregate module 15 as well as with the waste heat of the electrical and electronic units 16 additionally heated supply air ZL 'on the inner wall of the tower 10 and the gondola 11 leads.

In the summer months, the one of the simple air treatment device 3 to the aggregate module 15 delivered supply air flow ZL also the additional energy from the radiation of electrical and electronic units 16 in the aggregate module 15 record what at correspondingly high temperature of the outside air AL and after the additional heating by the air heater 31 for crystallizing the salt aerosols and separating the salt particles thus formed in the high-performance filter 32 to a critical temperature increase in the aggregate module 15 lead, if not a high limit temperature in the aggregate module 15 approved and / or possible overheating in the unit module 15 is accepted.

In addition, it should be noted that the wind power plant is not in operation for many hours of the year, for example during storms, light winds, accidents and maintenance. Even during these hours of the year, the greatest possible safety with regard to overpressure, salt-free, temperature-keeping, humidity and prevention of condensation on the aggregate module 15 and in the tower 10 as well as the gondola 11 discharged supply air ZL or heated ZL ', an emergency operation is required with the simple air treatment device 3 can only be adequately ensured by, for example, the air heater 31 the simple air treatment device 3 is connected to an electric afterheating device, which is fed in emergency mode from the supply network to which the wind energy system emits electrical energy in normal operation.

Furthermore, a temperature and humidity retention in the aggregate module 15 and inside the tower 10 and the gondola 11 Without thermodynamic treatment of the outside air AL or supply air ZL 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 aggregates 16 to a cooling liquid for heat dissipation and feeding the air heater 31 or an evaporator of the simple air treatment device 3 between full load and partial load fluctuations and in emergency mode, ie at standstill of Wind energy system, not available at all.

In the 5 to 6 is an improved air handling device 4 shown in detail below and explained in their function.

The improved air treatment device 4 contains according to 6 an evaporator 41, that of the conventional air treatment device 2 discharged, desalinated and dehumidified outside air AL is supplied, previously through the air inlet opening 14 from the surroundings of the tower 10 aspirated as moist and salty outdoor air AL and in the air treatment or desalination unit 2 according to 2 partially desalted and dehumidified. Furthermore, the improved air handling device includes 4 a condenser or a reheat coil 43 and a compressor 42 that together with the evaporator 41 Make a dehumidifying heat pump, and a high-performance filter 44 for salt separation. The one from the conventional reprocessing device 2 discharged, partially desalinated and dehumidified outside air flow AL is of the in the flow path of the outside air AL in the air treatment or desalination 2 according to 2 arranged outside air fan 25 to the improved air handling device 4 in which the outside air AL by means of the evaporator 41 is cooled to a lower level, wherein the absolute humidity of the outside air AL is lowered.

The cooling of the moist and saline outside air AL while reducing the absolute moisture content of the outside air AL, by the arrangement of a de-icing system in the evaporator 41 takes place at temperatures below freezing, takes place to the extent that by the subsequent reheating by the condenser or the reheat coil 43 a humidity value of the treated outside air AL of less than or equal to 40% relative humidity is achieved. By this process, the salt aerosols still contained in the outside air AL are crystallized and can by the downstream in the flow direction of the outside air AL high-performance filter 44 be deposited. After the dehumidification and desalination of the outside air AL, supply air ZL flows from the high-performance filter 44 according to 5 free and without special air distribution systems in or through the aggregate module 15 and through the upper part of the tower 10 to the gondola 11 and can be there due to leaks due to the outdoor air fan 25 of the air treatment or desalination device 2 produced excess pressure escape as exhaust air FL.

This process also ensures that the dehumidified and desalinated supply air ZL, even with total re-cooling on the temperature value of the outside air AL due to cooling on the way from the unit module 15 to the gondola 11 through the uninsulated steel walls of the tower 10 nowhere in the interior of the tower 10 the low level of the dew point, ie a relative humidity of 100%, can reach. For example, the value of the relative humidity in the entire interior of the tower 10 at 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.

Based on the in 7 illustrated Mollier-h, x-diagram is to the operation of the improved air treatment device 4 according to the 5 and 6 are explained with four temperature examples, in which a relative humidity of the outside air AL of 100% is assumed.

In the first example, the temperature T11 of the outside air AL = 20 ° C and is in the evaporator 41 cooled to a temperature T12 = 14 ° C. The absolute humidity of the outside air AL is reduced to about 10 g / kg. By subsequently heating the cooled and dehumidified outside air AL in the condenser or reheat coil 43 To a temperature T13 of about 32 ° C, the relative humidity of the outside air is reduced to about 35%, so that the salt aerosols contained in the outside air AL are substantially crystallized and the crystallized salt aerosols and contained in the outside air AL salt particles in the high-performance filter 44 can be separated.

The in the air treatment device 4 Dehumidified and desalinated outside air AL is supplied as supply air ZL to the unit module 15 and after flowing through the unit module 15 and recording of the electrical and electronic aggregates 16 radiated heat energy as heated supply air ZL 'in the interior of the tower 10 given by the inclusion of additional heat energy, a further increase in temperature with respect to the temperature T13, which is associated with a further decrease in the relative humidity. A re-cooling of the heated supply air ZL 'on the way through the interior of the tower 10 and the gondola 11 to the air outlet opening 13 , Where the heated supply air ZL 'is discharged as exhaust air FL to the environment, but can only be up to the value of the outside temperature T11 of 20 ° C, that is to say to the point T14, so that the air in the interior of the tower 10 and the gondola 11 can not fall back to the dew point line, that is, to the line 100% relative humidity, but according to the Mollier-h, x-diagram according to 7 remains at a value of relative humidity of only about 70%. It still remains unconsidered that by the absorption of heat energy in the aggregate module 15 an increase in temperature T13 he follows, so that the relative humidity is still above this value of 70%.

In the second example, a temperature T21 of the outside air AL of 14 ° C is assumed. The moist and saline outside air AL is along the dew point line in the evaporator 41 cooled to a temperature T22 of about 9 ° C and thereby lowered to an abso lute humidity of about 7 g / kg. By subsequent heating in the condenser or reheat coil 43 the dehumidification heat pump to a temperature T23 of about 25 ° C, the relative humidity of the outside air is reduced to about 38% and the crystallized salzaerosols and salt particles contained in the outside air AL in the high-performance filter 44 deposited.

In the third example, a temperature T31 of the outside air AL of 7 ° C is assumed. The moist and saline outside air AL is along the dew point line in the evaporator 41 cooled to a temperature T32 of about 2 ° C and thereby lowered to an absolute humidity of about 4 g / kg. By subsequent heating in the condenser or reheat coil 43 The dehumidification heat pump to a temperature T33 of about 14 ° C, the relative humidity of the outside air is reduced to about 40% and the crystallized salt aerosols and in the outside air AL salt particles contained in the high-performance filter 44 deposited.

In the fourth example, a temperature T41 of the outside air AL of -5 ° C is assumed. The moist and saline outside air AL is along the dew point line in the evaporator 41 cooled to a temperature T42 of about -12.5 ° C and thereby lowered to an absolute humidity of about 1 g / kg. By subsequent heating in the condenser or reheat coil 43 the dehumidification heat pump to a temperature T43 of about 1 ° C, the relative humidity of the outside air is reduced to about 25% and the crystallized salzaerosols and salt particles contained in the outside air AL can in the high-performance filter 44 be deposited.

Also in the second to fourth examples, that in the improved air treatment device 4 dehumidified and desalinated outside air AL as supply air ZL to the unit module 15 and after flowing through the unit module 15 and recording of the electrical and electronic aggregates 16 radiated heat energy as heated supply air ZL 'in the interior of the tower 10 issued. This is the in the air treatment device 4 dehumidified and desalinated outside air AL as supply air ZL to the unit module 15 and after flowing through the unit module 15 and recording of the electrical and electronic aggregates 16 radiated heat energy as heated supply air ZL 'in the interior of the tower 10 given by the inclusion of additional heat energy, a further increase in temperature compared to the temperatures T23, T33 and T43, which is associated with a further decrease in the relative humidity.

A re-cooling of the heated supply air ZL 'on the way through the interior of the tower 10 and the gondola 11 to the air outlet opening 13 , where the heated supply air ZL 'as exhaust air FL is discharged to the environment, but can only up to the value of the outside temperature T21 of 14 ° C, T31 of 7 ° C and T41 of -5 ° C, that is, to the points T24 , T34 and T44, so that the supply air ZL 'in the interior of the tower 10 and the gondola 11 can not fall back to the dew point line or 100% relative humidity, but according to the Mollier-h, x-diagram according to 7 only falls back to a value of relative humidity of about 60% to 70%. It still remains unconsidered that by the absorption of heat energy in the aggregate module 15 an increase of the temperatures T23, T33 and T43 takes place so that the relative humidity will still be above 60% to 70%.

The four in 7 Examples illustrated by a Mollier-h, x-diagram make it clear that the dehumidification process is solely due to the evaporation from the evaporator 41 , the condenser or reheat coil 43 and the compressor 42 formed dehumidification heat pump is completely achieved. The heat radiation in the aggregate module 15 arranged electrical and electronic units 16 and / or a possible after-heating from the waste heat of these units is an additional positive effect, which is not available at standstill of the wind power plant in weak or strong winds, in case of failure or shutdown for maintenance purposes. In this case, only the dehumidification heat pump can provide and provide the safety of salt-free and condensation-free, the entire system is independent of external heat or heating. This is significant in that downtime is more than 2000 hours per year.

In the 8th and 9 are two variants of a combination of an improved air handling device 4 with a conventional air treatment device 2 and are explained in more detail below.

In the first variant according to 8th is the over the air inlet opening 14 from the surroundings of the tower 10 by means of the outside air fan 25 sucked moist and salty outdoor air AL not via the conventional air treatment unit 2 according to

2 but only one first drop separator 21 a first simplified air handling unit 2 ' and then as dehumidified outside air AL the evaporator 41 supplied for cooling and dehumidifying. After heating in the condenser or reheat coil 43 The crystallized salt aerosols and salt particles contained in the outside air AL are in the high-performance filter 44 deposited, wherein the air flow through the in this embodiment, preferably on the suction side of the on the mist eliminator 21 reduced simplified air handling unit 2 ' and the improved air handling device 4 is arranged and the dehumidified and desalinated supply air ZL and in the high-performance filter 44 desalinated 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 gondola 11 is delivered.

In the arrangement according to 8th thus accounts for the coalescence 22 respectively. 23 according to 2 because by the out of the evaporator or cooler 41 , Condenser or reheat register 43 and compressor 42 Dehumidification heat pump formed a dehumidification and heating of the outside air AL in such a way that first water and thus salzerosols are deposited and crystallize the remaining salts after heating by means of the dehumidification heat pump when a value of relative humidity of less than or equal to about 40% is. Subsequently, the high-performance filter provides 44 for the precipitation of the crystallized salt.

As an alternative solution shows 9 the arrangement of both the two droplet separators 21 . 24 as well as a coalescence separator 22 in an air handling unit 2 '' , In this embodiment, that from the environment by means of the outside air fan 25 sucked outside air AL via a first droplet separator 21 , a coalescence separator 22 and a second mist eliminator 24 of the air treatment device 2 '' led there, partially dehumidified and desalted and then as partially dehumidified and desalinated outside air AL in 8th shown supplied dehumidification heat pump, where the outside air AL in the evaporator 41 cooled and dehumidified, in condenser or reheat coil 43 heated and the thus crystallized salt aerosols and contained in the outside air AL salt particles in the high-performance filter 44 be deposited before the dehumidified and desalinated supply air ZL in free air flow to the aggregate module 15 and as heated supply air ZL 'in the interior of the tower 10 and the gondola 11 is delivered.

The in the 8th and 9 on the suction side of the air treatment unit 2 ' respectively. 2 '' and the improved air handling device 4 arranged outside air fan 25 may alternatively also on the pressure side, ie before the first droplet 21 of the air treatment device 2 ' or before the first droplet separator 21 of the improved air handling unit 2 '' or between the air handling unit 2 ' respectively. 2 '' and the improved air handling device 4 to be ordered. The arrangement of the outside air fan 25 on the suction side of the air treatment unit 2 ' respectively. 2 '' and the improved air handling device 4 However, has the significant advantage that the outside air fan 25 not in moist air, but in relatively dry air, which is also free of salt, which offers advantages in terms of the corrosion behavior of the outside air fan 25 having.

In 10 is an optimized air treatment system 6 with an optimal air treatment device 5 and air ducts 75 . 76 in the aggregate module 15 illustrated, with the under all climatic conditions, in the year-round operation and in emergency mode with a stationary wind power plant, possibly via the air treatment unit 2 sucked moist and salty outdoor air AL dehumidifies, is filtered and desalted, a heat dissipation in the aggregate module 15 arranged heat-emitting electrical and electronic units 16 is carried out, ensures a positive pressure in the entire wind energy plant and a risk of corrosion is essentially excluded.

According to the schematic representation according to 10 is the sucked moist and salty outdoor air AL in the air treatment unit 2 only partially or coarsely desalted and partially dehumidified, the still humid and salty outdoor air AL 'an optimal air treatment facility 5 supplied and from this as a dehumidified and desalinated supply air ZL via a supply air duct 74 through the aggregate module 15 passed, without in contact with the air in the aggregate module 15 to arrive, and above the aggregate module 15 to the free space above 100 of the upper part of the tower 10 issued.

At the end of the supply air duct 74 Optionally, a postheater or heat exchanger 8th be arranged with control valve, with which the temperature in the upper area of the tower 10 and in the gondola 11 is regulated. The heat exchanger is fed 8th from the waste heat of the heat generating electrical and electronic units 16 in the agregate module 15 , The heat exchanger 8th may alternatively or optionally also directly in or on the optimized air treatment device 5 or at any other point in the supply air duct 74 to be ordered. In addition, it is possible, the Nachheizregister or the heat exchanger 8th as static acting element free in the tower 10 set up when you're on can dispense with influencing the flow behavior.

The effect and positive consequences of the heat exchanger 8th consist in that to avoid condensation within the tower 10 and the gondola 11 the air over the heat exchanger 8th is heated so far, ie 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 gondola 11 the dew point is not reached. Preferably, a sensor for the temperature measurement and control in the nacelle 11 arranged in front of the air outlet due to the generated overpressure.

However, this effect is achieved only in conjunction with a arranged in the outside air flow AL evaporator a dehumidification heat pump, the first with a slight cooling causes a significant dehumidification (elimination by condensation), so that the air at full recooling when flowing through the tower 10 due to the cooling of the tower walls to the temperature value of the outside air does not fall back to the humidity characteristic 100%, but at the same low temperature can only drop to 80% relative humidity.

Due to the hermetically separated guidance of two air streams in the optimized air handling unit 5 , of which the first flow path according to 11 from the air inlet 14 via an air treatment unit with recuperative heat recovery system 51 , Preferably a plate heat exchanger, but alternatively also a heat pipe or a dehumidification heat pump is guided, during the heat-exchanging connection with the first flow path stationary second flow path in a closed circuit through the aggregate module 15 leads and by the heat emission of the electrical and electronic units 16 absorbed heat energy via the air treatment unit with recuperative heat recovery system 51 to the first flow path, of which excluding the aggregate module 15 heated, dehumidified and desalinated air with overpressure to the interior 100 of the tower 10 and the gondola 11 is delivered. This ensures that the still contaminated with salt outside air AL 'no longer free through the aggregates module 15 flows 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 air treatment unit 2 discharged outside air AL ', but also takes over the cooling of the unit module 15 through targeted air extraction from the individual floors or platforms of the aggregate module 15 via circulating air exhaust air ducts 76 and a targeted air supply via circulating air supply air ducts 75 into the individual floors or platforms of the aggregate module 15 , If the supply air ZL (UL) of the circulating air UL does not reach the individual levels of the unit module 15 fed, but blown example, in the lower floor and deducted in the upper floor, so is a corresponding air duct between the floors of the unit module 15 intended.

In this recirculation process, the energy above that in the optimized air treatment device 5 arranged plate heat exchanger 51 between the outside airflow 1 and in the air ducts 75 . 76 guided circulating air flow UL exchanged. The outside air flow AL 'or supply air flow ZL thus indirectly cools the recirculating air flow UL. The recirculating air flow UL gives the heat resulting from the surface heat emission of the electrical and electronic units 16 arises, to the supply air flow ZL, so that the heated supply air flow ZL '' according to 10 preheated in the upper tower 10 and with it in the gondola 11 arrives. At extremely low temperatures, additional reheating can be achieved through the optional heat exchanger 8th respectively.

But even without the arrangement of air ducts 75 . 76 for the targeted guidance and delivery of the recirculating air flow UL to the in the individual levels or floors of the unit module 15 arranged electrical and electronic units 16 results in a significant improvement, because the recirculating air flow UL, passing through the plate heat exchanger 51 hermetically from that in the supply air duct 74 led supply air flow ZL is separated, contains no salt particles or aerosols, is also cooled and the surface heat of the electrical and electronic units 16 dissipates. The air ducts 75 . 76 for the circulating air flow UL are therefore not mandatory to arrange, but it is obvious that a targeted supply and exhaust air of the circulating air flow UL is the more effective solution

The plate heat exchanger 51 in the optimized air treatment facility 5 separates the outside air flow AL 'and supply air flow ZL hermetically from the recirculation air flow UL and thus ensures that a free flow through the unit module 15 and so that contamination by saline, moist outside air AL 'can not take place. The aggregate module 15 As a result, it is located in a salt-free zone of the tower body.

Alternatively, the aggregate module 15 also below the air inlet opening 14 be arranged for the outside air AL, so that the optimized air treatment facility 5 the heated and desalinated air directly to the upper, free part of the tower 10 while the recirculating air flow UL into the below the optimized air treatment device 5 arranged aggregate module 15 is discharged, where the circulating air flow UL from the electrical and electronic units 16 heat dissipated and this over the plate heat exchanger 51 in the hermetically separated supply air flow ZL and thus in the optionally on the Nachheizregister or the heat exchanger 8th heated supply air flow ZL '' in the interior of the tower 10 feeds.

The optimized air treatment device 5 does not necessarily have to be in the area of the aggregate module 15 can be arranged, but can be arranged at any other place, in particular, because through air ducts targeted air introduction into the aggregate module 15 and air extraction from the unit module 15 can be generated.

Also, the in 10 registered supply air duct 74 not necessarily on the upper deck of the aggregate module 15 but can also go beyond that to the inside of the tower 10 be extended.

In the 11 as an airflow and system diagram and in 12 in a longitudinal section through a corresponding air conditioner illustrated air treatment device 5 shows a housing 50 with an outside air opening for intake outside air AL, a supply air / overpressure opening for discharging the heated supply air flow ZL to the part of the tower 10 , the above or outside of the aggregate module 15 is located, as well as an exhaust / return air duct or channels 76 and a circulating air / supply air duct or channels 75 , via which the circulating air in and out of the aggregate module 15 to be led. In the case 50 the air treatment device 5 is a plate heat exchanger 51 arranged with hermetically separated, in heat-exchanging connection flow paths, of which the first flow path from the environment of the tower 10 over the air inlet opening 14 sucked outside air AL via an evaporator or cooler 53 , the plate heat exchanger 51 , a capacitor 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 leads, during the heat-exchanging connection with the first flow path stationary second flow path through a circulating air fan 56 is generated, in a closed circuit from the aggregate 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 aggregate module 15 is guided and by the heat emission of the electrical and electronic units 16 absorbed heat energy through the plate heat exchanger 51 emits to the first flow path. The first flow path leads through the supply air duct 74 excluding the aggregate module 15 the heated supply air ZL with overpressure to the interior of the tower 10 and the gondola 11 from.

To the number of plates of the plate heat exchanger 51 set to be used in the fresh air supply air flow for energy exchange or to be passed to the energy exchange, the plate heat exchanger 51 at the entrance of the cooled outside air AL 'bypass flaps 52 on their adjustment thus influence on the energy exchange and thus on the temperature and / or humidity behavior of the air treatment device 5 can be taken. This allows the bypass valves 52 of the plate heat exchanger 51 in a temperature and humidity control of the optimized air treatment system 6 be included.

In the 11 and 12 not shown is the outside air fan 25 according to the embodiments described above. This can be on the pressure side of the optimized air treatment system 6 be arranged when, for example, part of the air treatment device 2 respectively. 2 ' or 2 '' is and the optimal air treatment device 5 is retrofitted. Advantages, however, provides the arrangement of the outside air fan 25 on the suction side, ie in the flow direction of the outside air AL to the supply air ZL behind the air treatment device 5 because it is here in dry, salt-free air, whereby the risk of corrosion is significantly reduced and only low demands on the material quality of the outdoor fan 25 are to be made. In addition, the arrangement of the outside air fan allows 25 on the suction side placements of the outside air fan 25 from the aggregate module 15 over all the decks of the tower 10 to the gondola 11 as a site possible and suitable.

Since the offshore wind energy plant is permanently exposed to extreme weather influences with all temperature influences and wind movements, condensation phenomena can occur on the inside of the tower walls, in particular if the temperature and humidity conditions of the supply air ZL are in the vicinity of the so-called dew point. Such conditions occur, for example, when on the north side of an icy wind the tower 10 flows and the tower 10 on the south side is heated by solar radiation. To reduce the risk of condensation within the entire tower 10 exclude or at least reduce, the air treatment device 5 from the evaporator or cooler 53 and the capacitor or reheat register 55 and a compressor 54 formed dehumidifying heat This pump is designed to achieve dehumidification of 1 g / kg air or more. 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, ie as far as possible from the dew point.

A dehumidification of 1 g / kg already causes, with re-cooling the into the interior of the tower 10 blown supply air ZL on the way to the outlet opening 13 in the gondola 11 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 no condensation inside the tower 10 and the gondola 11 consists. 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 11 Therefore, the outside air immediately after the exit from the plate heat exchanger 51 with the energy from the dehumidification process via the capacitor or the reheat register 55 additionally heated, which in turn causes an even more favorable, namely a lower value in the relative humidity. The in 19 illustrated Mollier-h, x-diagram shows that the air, the tower 10 and the gondola 11 is flowed through and cooled again on the tower walls, even with a one hundred percent cooling effect can not fall below the achieved by this process low dew point. At best, the cooling air flow can rise to a relative humidity of 80% at most.

Since weathering factors can produce the entry points in such a way that the circulating air flow UL within the plate heat exchanger 51 reaches the dew point and separates condensate, a positive side effect occurs. Whenever the circulating air flow UL does not reach the dew point and the outside air flow AL 'has a lower absolute humidity than the circulating air flow UL, the partial pressure causes a reduction of the moisture content in the circulating air flow UL and thus a drying in the aggregate module 15 of the tower 10 , This means that the partial pressure always a favorable flow to the area of lower pressure, ie from the aggregate module 15 to the tower 10 causes.

The arrangement of the evaporator 53 and capacitor 55 is not mandatory at the air inlet or outlet of the plate heat exchanger 51 required, but can also be somewhere within the channel system of the tower 10 blown supply air flow ZL, ie, within the supply air duct 74 be provided.

Will the capacitor 55 not in the flow direction after the plate heat exchanger 51 arranged, but for example immediately after the evaporator 53 , so the dehumidification, ie, the moisture reduction results in the same way. However, 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 previously based on the 5 to 9 described improved air treatment device 4 With regard to the functions of dehumidifying, reheating, desalting, avoiding condensation in the entire wind power plant, reducing corrosion and emergency heating during system downtime by the dehumidification heat pump system already represents a significant improvement of conventional dehumidification and desalination by means of the air treatment unit or desalination unit 2 without providing for the improved air handling equipment 4 high investment costs to book. In particular, the improved air handling equipment has been used 4 compared to the above with reference to the 10 and 11 described first embodiment and the following with reference to the 12 to 29 described further embodiments of an optimal air treatment systems 6 with optimal air treatment device 5 on air ducts 75 . 76 in the aggregate module 15 and to an air treatment unit with heat recovery system (plate heat exchanger) 51 dispensed so that in the improved air treatment system 4 no targeted air routing via air ducts 75 . 76 in the aggregate module 15 and thus no targeted cooling as well as in connection with the elimination of the air treatment unit with heat recovery system 51 no hermetic separation between the circulating air flow in the unit module 15 and the outside air supply air flow is given. In the improved air treatment system 4 form the aggregate module 15 and the interior of the tower 10 as well as the gondola 11 a unit in terms of airspace.

Nevertheless, those in the 10 to 29 described optimal air treatment systems 6 arranged elements and components for air flow and dynamics in the tower 10 such as the arrangement of nozzles, heaters, other fans for re-generating a propulsion jet, and the like, also in conjunction with the above-described improved air handling equipment 4 be used.

There is also a cooling of the heat giving electrical and electronic units 16 in the aggregate module 15 with free flow of supply air ZL without air ducts instead. It is done waiving air ducts only with lower efficiency than a targeted cooling using air ducts.

By the arrangement of the plate heat exchanger 51 in the optimal air treatment facility 5 is a hermetic separation of the outside air supply air flow, that of the air inlet opening 14 through the supply air duct 74 from the aggregate module 15 isolated by the interior 100 of the tower 10 and the gondola 11 to the air outlet opening 13 is guided, guaranteed by the recirculation flow, the targeted on the air ducts 75 . 76 into the individual floors of the aggregate module 15 is guided and the heat-emitting electrical and electronic units 16 discharged heat dissipated. As a result, no residual moisture and no residual salt content in the aggregate module 15 penetration.

The air ducts 75 . 76 In addition, a targeted air flow and targeted cooling, so that the heat-emitting electrical and electronic units 16 be effectively cooled regardless of their location. The at the plate heat exchanger 51 provided bypass flap 52 It also makes it possible to variably control the energy exchange for temperature and / or humidity control. While the outside supply air flow through the outside air fan 25 is promoted, generates the independent air circulation fan 56 the circulating air flow, wherein the variable speed circulating air fan 56 generates variable volume flows of the recirculating air flow, thus also the heat transfer in the plate heat exchanger via this path 51 and thus the temperature and / or humidity can be controlled or regulated.

13 shows a variant of the configuration of the optimal air treatment device 5 with one in the exhaust / return air line 76 the circulating UL arranged Reheat register 62 in the form of a condenser, on the 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 energy plant, from the condenser 55 is switched so that the from the evaporator or cooler 53 , Condenser or reheat register 55 and compressor 54 dehumidification heat pump in the outdoor air supply air flow AL / ZL to the unit module 15 discharged supply air ZL (UL) of the circulating air UL of the second flow path heated. The energy for this heating operation is supplied by other offshore wind power plants operated in the network.

As is known, 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 found 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%. In order to prevent uncleaned air or air with an inadmissibly high salt content in the aggregate module as a result of leaks or other circumstances 15 penetrates, an embodiment of the air treatment device according to 14 be used, in addition to the plate heat exchanger 51 that is from the evaporator / cooler 53 , Compressor 54 and capacitor / rehab register 55 composite dehumidification heat pump, the high-efficiency 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.

15 shows a schematic longitudinal section through the housing 50 the in 14 Air treatment device shown as air guide and system scheme 5 ,

To the air resistance caused by the arrangement of the high-performance filter 61 in the circulating air flow UL conditionally, in the air treatment device 6 and thus the energy consumption of the air treatment device 5 lower, the high-performance filter 61 in the embodiment of the air treatment device according to 16 in a bypass 60 arranged for selective connection or disconnection, for example, depending on the humidity. The bypass 60 has two louvers 602 . 603 depending on a moisture measurement, the proportion of the circulating air flow UL set via the bypass channel 601 and with the high-performance filter 61 is directed.

A similar bypass can also 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 be provided.

In the 17 Embodiment of an optimal air treatment device shown in an air guide and system scheme 5 differs from the air treatment device 5 according to 14 in that the dehumidification heat pump has two capacitors or reheat registers 55 and 59 comprising, of which a first capacitor 55 in the flow direction of the outside air supply air flow in front of the plate heat exchanger 51 and the second capacitor 59 in the flow direction of the outside air supply air flow to the plate heat exchanger 51 is arranged. By switching from the first capacitor 55 on the second capacitor 59 or by stepwise connection of the second capacitor 59 to the first capacitor 55 the supply air flow ZL after the plate heat exchanger 51 be heated further.

This mutual circuit of the capacitors 55 . 59 has the advantage that the different requirements between summer and winter operation can be better met. As the efficiency of the plate heat exchanger 51 or whose heat transfer is determined by the temperature difference, the first capacitor 55 preferably used in winter, while the second capacitor 63 preferably used in the summer. Depending on the requirements, both capacitors can be used 55 . 59 be operated in partial load operation, with both capacitors 55 and 59 be controlled automatically in reciprocal mode or with variable part loads.

Another possibility for temperature control is the circulating air fan 56 provided 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 through the plate heat exchanger 51 is transferred to the outside air supply air. This indicates the air treatment device 5 next to the bypass flaps 52 at the plate heat exchanger 51 and the mutually adjustable capacitors 55 . 59 another influencing factor for temperature and humidity control.

The air treatment device according to 18 has a dehumidification heat pump system from an evaporator or cooler both in the outside air supply air 53 , Condenser or reheat register 55 and compressor 54 as well as in the circulating air stream a dehumidification heat pump system from an evaporator or cooler 62 , Condenser or reheat register 64 and compressor 63 on, in the exhaust duct 76 the circulating air UL in the flow direction in front of the high-performance filter 61 is arranged. This results in the possibility of eliminating salt particles and aerosols present in the circulating air flow UL, which may be due to leaks during assembly or the like in the aggregate module 15 reach.

Based on the in 19 shown Mollier-h, x-diagram to the operation of the air treatment device according to 18 be explained in summer and winter operation. 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.

In the first step, both for the outside air AL and for the recirculating air UL cooling takes place with simultaneous dehumidification. In the second step, reheating (reheat) takes place through the condenser both for the outside air AL and for the recirculating air UL 55 respectively 59 according to the dehumidification heat pump principle. In the third step takes place for the outside air AL further heating by the heat transfer from the warmer, through the plate heat exchanger 51 guided circulating air flow UL. At the same time in the third step for the circulating air flow UL, which is in the relatively dry area, that is below or around the 40% relative humidity line, the filtering and thus the elimination of the salt particles from the recirculating air flow UL. In the fourth step, the filtering and elimination of the salt particles from the outside air supply air flow, after the Au ßenluftstrom heat from the transfer of the plate heat exchanger 51 has recorded.

According to the Mollier-h, x-diagram 19 It can be seen that the outdoor air supply air flow both in summer and in winter operation respectively reaches the minimum relative humidity of less than or equal to about 40% and even falls below, which is the prerequisite for the formation of salt particles from the aerosols the high performance filters 57 . 61 be excreted.

Of course, in the arrangement of the air treatment device according to 18 also a division of the arranged in the outside air supply air flow capacitor in a first capacitor 55 in the flow direction of the outside air in front of the plate heat exchanger 51 and a second capacitor 59 in the outside air supply air flow behind the plate heat exchanger 51 arranged and in alternating operation with the first capacitor 55 analogous to the embodiment of the air treatment device according to 17 operate.

This in 20 shown air duct and system diagram of another embodiment of the optimal air treatment device 5 differs from the embodiment according to 8th by the arrangement of a bypass 70 , that of the supply air duct 74 and thus from the supply air flow ZL leads to the recirculating air flow UL, where he is between the from the evaporator or cooler 62 , Condenser or reheat register 64 , Compressor 63 formed dehumidifying heat pump system and the high-performance filter 61 is connected to the overpressure in the circulating air flow UL.

With this embodiment of the air treatment lung device 5 that is achieved by the aggregate module 15 flowing circulating air UL is not contaminated by currents from other areas of the wind turbine with saline air. The required amount of bypass air is very small and does not appreciably affect the moisture content of the circulating air UL and only prevents negative flows from the area of the tower 10 the wind turbine or the air inlet opening 14 into the aggregate module 15 penetrate, so that the required amount of air is only slightly.

Regardless of the temperature level of the over the bypass 70 Guided recirculation this will not significantly affect the temperature of the circulating air UL due to their extremely small amount. In addition, the over the bypass 70 Guided recirculation part taken from the supply air flow ZL, which is already energy in the flow through the plate heat exchanger 51 has recorded. The supply of the bypass air flow to the circulating air UL can be arranged at any point of the air ducting system, for example, the bypass air flow also directly into the aggregate module 15 flow without air ducts.

In the 21 to 27 are further embodiments of an optimal air treatment device 5 an optimized air treatment system for normal operation and emergency operation 6 shown, which can be selected adapted to the respective requirements such as environmental conditions, size and power of the wind turbine, investment costs and the like. The working principle common to these embodiments will follow the description of the Luftführungs- and systems of the systems 21 to 27 described in more detail.

This in 21 illustrated embodiment of an air treatment device 5 differs from the air treatment device according to 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 the air treatment device 5 , From the supply air duct 74 branches a bypass 701 from the supply air ZL to the unit module 15 or optionally via the bypass 702 to the circulating air flow UL, both bypass guides via a motor bypass flap 700 controlled, so that the supply air to the overpressure control in the aggregate module 15 can be regulated. The evaporator 53 the outside air dehumidification heat pump system preferably has a defrosting device, so that the entire performance of the evaporator 53 is provided by two separate evaporator systems.

In the embodiment of the air treatment device according to 22 is analogous to the embodiment according to 17 a division of the condenser of the outside air dehumidification heat pump system in two capacitors or reheat register 55 and 59 provided, of which the first capacitor 55 in the flow direction of the outside air supply air flow in front of the plate heat exchanger 51 and the second capacitor 59 in the flow direction of the outside air supply air flow to the plate heat exchanger 51 is arranged. By switching from the first capacitor 55 on the second capacitor 59 or by stepwise connection of the second capacitor 59 to the first capacitor 55 the supply air flow ZL after the plate heat exchanger 51 be heated further.

This in 23 illustrated air duct and system diagram of a further embodiment of the invention optimal air treatment device 5 is different from the one in 22 illustrated embodiment by the optional arrangement of a bypass 71 in the flow path of the circulating air flow UL and a bypass 72 in outdoor air supply air flow path AL / ZL. The bypass 71 in Umluftströmungsweg UL has bypass valves 711 . 712 and a bypass line 713 on while bypassing 72 in outdoor air supply air flow path AL / ZL bypass flaps 721 . 722 as well as a bypass line 723 from the outside air AL to the supply air ZL.

The bypasses provided in the outdoor air supply air flow AL / ZL and in the recirculation air flow UL 71 . 72 allow the air flows through the bypass lines 713 respectively 723 on the high-performance filters 57 . 61 Pass by, if the relative humidity of less than or equal to about 40% is not reached or can be maintained. The independently controllable bypass flaps 711 . 7182 respectively 721 . 722 can be adjusted by a control device in the respectively required position, so that the air flows at favorable humidity values either the high-performance filter 57 . 61 flow through or via the bypass lines 713 . 723 on the high-performance filters 57 . 61 passed by. This ensures that salt crystals in the high-performance filters 57 . 61 accumulated and stored on the "dirty" side, do not fall back to aerosols at elevated humidity values and on the "pure" side of the high-performance filter 57 . 61 penetrate and about the increased humidity in the aggregate module 15 or in the tower 10 or the gondola 11 be carried in.

This in 24 illustrated air duct and system diagram of a further embodiment of the optimal air treatment device according to the invention 5 differs from the air treatment devices described above the additional arrangement of dehumidification heat pump systems in the outdoor air supply air flow AL / ZL and in the recirculating air flow UL. That in the flow path of the circulating air flow UL before from the waste heat of the electrical and electronic units 16 in the agregate module 15 powered heater 65 arranged dehumidification heat pump system consists of the evaporator / cooler 62 , Compressor 63 and a first capacitor 64 , In the outside air supply air flow path that is from the evaporator / cooler 53 , the compressor 54 and a first capacitor / reheat register 55 or a second capacitor / reheat register 59 arranged with mutual operation existing dehumidification heat pump system.

A second condenser / reheat register connected to the dehumidification heat pump system arranged in the circulating air flow UL 66 is the first capacitor / rehab register 65 assigned and operated together with this or mutually. The evaporator arranged in the dehumidification heat pump system of the outside air supply air flow AL / ZL 53 preferably has a defrosting device, which is why the entire performance of the evaporator 53 is applied by two optional separate evaporator parts.

In the 24 illustrated air treatment device with dehumidification heat pump systems in the circulating air flow UL and outdoor air supply air flow AL / ZL can as emergency heating, for example, to frost-free air treatment device 5 , or for additional desalination and dehumidification at low temperatures and downtime of the wind turbine can be used. The dehumidification heat pump systems in the fresh air supply air flow AL / ZL and recirculated air flow UL offer a very high efficiency with lowest power consumption high heat output, whereas an electric heater with the same heat output would cause more than five times the power consumption. By the arrangement of a second capacitor 66 the circulating air dehumidification heat pump system in the outside air supply air flow AL / ZL can be switched depending on the requirement and heat demand, the energy output from 0 to 100% or regulated. The dehumidification heat pump system in the outdoor air supply air flow AL / ZL also has two condensers 55 . 59 so that the heat energy as needed in the air direction before or after the plate heat exchanger 51 and can be regulated from 0 to 100%.

In the 25 to 27 are different variants of a combination of the air treatment device 5 according to 24 with a conventional air treatment device 2 according to 2 shown.

In the embodiment according to 25 consists of the conventional air treatment unit 2 from a first droplet separator 21 a coalescence separator 22 and a second mist eliminator 24 in the outside air flow AL between the air inlet opening and the optimal air treatment device 5 are arranged. The outside air fan 25 is in this embodiment, the pressure side of the air treatment device 5 between the first droplet separator 21 and the coalescer 22 arranged.

25 shows in an alternative embodiment, the arrangement of the outside air fan 25 in dashed line on the suction side of the air treatment device 5 where is the outside air fan 25 not in moist, salty or only roughly dehumidified and desalinated outside air AL, but in dry, salt-free supply air, which increases the risk of corrosion of the outside air fan 25 considerably reduced and thus lower demands on the material quality of the arranged on the suction side outside air fan 25 and other components, optionally in the direction of air flow, in front of or behind the air treatment device 5 can be arranged, reduced. This is associated with a much cheaper construction of the optimized air treatment system.

The embodiment according to 26 differs from the arrangement according to 25 to the effect that the outside air fan 25 suction side of the air treatment device 5 is arranged.

In the arrangement according to 27 consists of the air treatment device 2 only from a droplet separator 21 , the suction side of the outside air fan 25 is arranged, in turn, the pressure side of the air treatment device 5 is arranged. The coalescence separator 22 the arrangement according to the 25 and 26 was removed here as its task by the air treatment facility 5 with taken over.

The in the optimized air treatment system 6 used components such as dehumidification heat pump systems (evaporator, condenser / reheat, heating coil, etc.) can for functional reasons or system or process-related both in the flow direction before and after the plate heat exchanger 51 arranged arbitrarily and combined with each other. In addition, 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 to the dehumidification heat pump systems as required, depending on where the electric and electronic units are 16 emitted heat their best effect achieved by switching and / or stepped or continuous control. In so far show the optimized air treatment systems described above 6 just an example of many arrangement options.

• – der Verdampfer 53 ist vorzugsweise mit einer Enteisungseinrichtung ausgestattet, da im Offshore-Bereich bei niedrigen Temperaturen und hoher Luftfeuchte im Bereich des Gefrierpunktes und darunter Vereisungsgefahr aufgrund der niedrigen Verdampfungstemperatur besteht. Enteisungseinrichtungen sind aus der Entfeuchtungswärmepumpenkonstruktion bekannt und bedürfen daher keiner näheren Beschreibung. In vorteilhafter Ausführungsform ist der Verdampfer mit Enteisungsfunktion 53 zweiteilig für einen Teillastbetrieb ausgebildet;
• – der Verdampfer 53 bewirkt immer dann, wenn die Eintrittstemperatur, d. h. die Außentemperatur, an der Taupunktlinie, d. h. bei 100% relativer Feuchte, liegt und damit eine erhöhte Kondensationsgefahr innerhalb der Windenergieanlage auftreten kann, eine Temperaturabsenkung entlang der Taupunktlinie und scheidet dabei Wasser aus. Dadurch ergibt sich eine Reduzierung der absoluten Feuchte, so dass die Gefahr der Kondensation gebannt ist. Dabei wird eine Reduzierung der relativen Feuchte in der Weise angestrebt, dass in Verbindung mit dem Kondensator beziehungsweise der Reheat-Einrichtung 55 und gegebenenfalls durch ergänzende Heizeinrichtungen auf der gesamten Strecke des Strömungsweges der Zuluft bis zur Gondel 11 und innerhalb der Gondel 11 selbst bei totaler Rückküh lung des Zuluftstromes insgesamt oder punktuell durch die enorme Fläche des Turmes 10 der Taupunkt nicht wieder erreicht wird und Kondensation auf dem gesamten Strömungsweg nicht entstehen kann. Wesentlich hierbei ist, dass zur Erreichung dieses Zieles die Leistungsgröße und damit der Energieverbrauch der Entfeuchtungswärmepumpe äußerst gering ist, was insbesondere für den nachstehend beschriebenen Notbetrieb von Bedeutung ist, weil dann eine Stromversorgung aus dem von der Windenergieanlage im Normalbetrieb gespeisten Netz erfolgen muss, da die Windenergieanlage bei Stillstand keine Energie erzeugt. Das im Mollier-h,x-Diagramm dargestellte Beispiel zeigt, dass bereits eine geringe Entfeuchtung von nur 1 g/kg lediglich 8 kJ ausmacht. Nach der Erwärmung durch den Kondensator beziehungsweise das Reheat-Register 55 und nach gegebenenfalls weiterer Nachheizung und anschließender totaler Rückkühlung auf den Außenluft-Temperaturwert liegt die relative Luftfeuchtigkeit dann bei circa 80% relativer Feuchte, so dass die Kondensationsgefahr beseitigt ist. Bei Feuchtewerten oberhalb von ca. 80 bis 90% relativer Feuchte kann eine Kondensation durch Abkühlung an den Turmwandungen nicht auftreten, so dass dieser Bereich als unkritisch angesehen werden kann. Deshalb muss die Entfeuchtungswärmepumpe bei dieser Wettersituation nicht zwingend betrieben werden, sondern erfüllt lediglich optional einen zusätzlichen Zweck, nämlich die Aufheizung der Luft auf Temperaturbereiche, die das in Aerosolen gelöste Salz kristallisieren lassen, was mit dem Erreichen der 40% Feuchte Linie erfolgt und damit eine wirksame Filterung ermöglich. Der Kompressor 54 ist über Rohrleitungen und Regeleinrichtungen mit dem Verdampfer 53 und dem Kondensator 55 verbunden und kann innerhalb oder außerhalb des Luftstromes stehen.

The in the 10 to 27 illustrated optimal air treatment device 5 an optimized air treatment system 6 , which is intended and suitable for both normal operation and for emergency operation, facing the simple air treatment device 3 according to the 3 and 4 and the improved air handling device 4 according to the 5 to 9 the following features and functions:
In normal operation, when the wind turbine is operating and generating power, the outside air AL is from the outside air fan 25 of the conventional air treatment device 2 to the air treatment device 5 transferred and first flows through the evaporator 53 which has the following features or functions:

• - the evaporator 53 is preferably equipped with a defrosting device, as 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. In an advantageous embodiment, the evaporator is with de-icing function 53 formed in two parts for a partial load operation;
• - the evaporator 53 causes whenever the inlet temperature, ie the outside temperature, at the dew point line, ie at 100% relative humidity, and thus an increased risk of condensation can occur within the wind turbine, 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. In this case, 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 supplementary heating devices on the entire route of the flow path of the supply air to the nacelle 11 and inside the gondola 11 even with total recirculation of the supply air flow as a whole or in places through the enormous area of the tower 10 the dew point is not reached again and condensation on the entire flow path can not occur. It is essential that in order to achieve this goal, the performance and thus the energy consumption of the dehumidification heat pump is extremely low, which is particularly important for the emergency operation described below, because then a power supply must be made from the network fed by the wind turbine in normal operation, as the Wind turbine generates no energy at standstill. The example shown in the Mollier-h, x-diagram shows that even a low dehumidification of only 1 g / kg only accounts for 8 kJ. After heating by the condenser or the reheat register 55 and after optionally further reheating and subsequent total recooling to the outside air temperature value, the relative humidity is then at about 80% relative humidity, so that the risk of condensation is eliminated. At humidity values above approx. 80 to 90% relative humidity, condensation due to cooling on the tower walls can not occur, so that this range can be regarded as uncritical. Therefore, 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 about piping and control equipment with the evaporator 53 and the capacitor 55 connected and can be inside or outside the air flow.

After the dehumidifying and cooling process, the outside air AL flows through the condenser or the reheat register 55 and is heated there in a first stage again. Subsequently, the outside air flow AL absorbs further heat energy during the flow through the plate heat exchanger 51 on, which is discharged from the exhaust air of the circulating air flow UL. The plate heat exchanger separates 51 the outside air flow AL hermetically from the circulating air flow UL.

At the outlet of the plate heat exchanger 51 Under normal operating conditions, the supply air flow has reached a temperature that is less than or equal to approx. 40% relative humidity in the humidity range. The salzerosols are crystallized by this process and can by the reshaped high-performance filter 57 be deposited.

In the event that the humidity line of less than or equal to about 40% relative humidity is not reached, an additional heating device according to the in 21 to 27 illustrated optimal air treatment facilities 5 provided, which is preferably an electric heater, because in particular a heating must be provided in emergency operation.

In addition, several heating devices can be provided, for example in normal operation from the waste heat of the electrical and electronic units 16 in the aggregate module 15 be fed in conjunction with the arrangement of an additional electric heater.

By means of preferably with bypass valves 52 provided plate heat exchanger 51 can in conjunction with a control device of the optimal air treatment device 5 be influenced on the temperature and humidity values, because it variable energy amounts for energy exchange or energy transfer are available.

The the high performance filter 59 leaving dehumidified and desalinated supply air ZL can through the supply air duct 74 through the aggregate module 15 through the tower 10 and to the gondola 11 be guided, with the risk of condensation and increased corrosion within the tower 10 and the gondola 11 eliminated by salzerosols. Further measures for air treatment and air flow in the tower 10 and in the gondola 11 be based on the 28 to 34 described.

• – Zunächst kann in einem ersten Schritt der regelbare Umluftventilator 56 auf einen reduzierten Volumenstrom zurückgefahren werden, was als variabler Vorgang in Abhängigkeit von den Temperatur- und Feuchte-Sollwerten durchgeführt werden kann. Bei geringerem Volumenstrom werden sowohl eine höhere Ablufttemperatur als auch eine geringere relative Feuchte der Umluft UL erreicht;
• – da bei Temperaturen um den Gefrierpunkt und gegebenenfalls darunter eine starke Abkühlung durch die große Fläche der Turmwandungen im Aggregatemodul 15 stattfindet, wird in den Ausführungsformen der 21 bis 27 eine zusätzliche Heizeinrichtung 65 vorgesehen, die beispielsweise aus der Abwärme der elektrischen und elektronischen Aggregate 16 im Aggregatemodul 15 gespeist wird und die die Luft des Abluftstromes Ab(UL) der Umluft UL in Verbindung mit einem Regelventil auf die erforderliche Temperatur aufheizt. Diese Einrichtung ist auch aus Sicherheitsgründen vorgesehen, damit die Temperatur nicht unkontrolliert durch äußere Einflüsse absinkt und damit die erforderliche Feuchte von kleiner oder gleich ca. 40% relativer Luftfeuchte auch in derartigen Wettersituationen erreicht werden kann.

In recirculation flow path through the aggregate module 15 promotes the infinitely variable circulating air fan 56 the exhaust air flow Ab (UL) and the supply air flow ZL (UL) of the circulating air UL in the circuit. The exhaust air flow Ab (UL) is determined by the heat emission in the aggregate module 15 arranged electrical and electronic units 16 heated, so that in general, a humidity state of the circulating air UL is reached, which allows the filtration of crystallized Salzerosole. Should this not be the case, for example, in winter, when at extremely low temperatures the heating in the aggregate module 15 is already greatly reduced by cooling off on the tower walls, the 40% luminous flux can be achieved by the two following devices or functions:

• - First, in a first step, the controllable circulating air fan 56 be reduced to a reduced flow rate, which can be performed as a variable operation in response to the temperature and humidity setpoints. At a lower volume flow both a higher exhaust air temperature and a lower relative humidity of the circulating air UL are achieved;
• - Because at temperatures around the freezing point and optionally below a strong cooling by the large area of the tower walls in the aggregate module 15 takes place in the embodiments of the 21 to 27 an additional heating device 65 provided, for example, from the waste heat of the electrical and electronic units 16 in the aggregate module 15 is fed and 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.

After the exhaust air flow Ab (UL) of the circulating air UL has reached the required temperature and through the provided in the circulating air flow path high-performance fine filter 61 was cleaned, the exhaust air Ab (UL) flows through the plate heat exchanger 51 and indirectly dissipates the heat energy to the outside air supply air flow AL / ZL. The infinitely variable circulating air fan 56 now promotes the recirculation air flow UL as supply air flow ZL (UL) to the unit module 15 , optionally in the individual floors of the unit module 15 ,

Now a supply air flow ZL (UL) of the circulating air UL is available, which is sufficiently cooled, but on the other hand also has a sufficient minimum temperature at extremely low outside temperatures, thus cooling the unit module 15 prevented in the recirculation principle again the waste heat in the unit module 15 arranged electrical and electronic units 16 due to heat dissipation and the aggregate module 15 over the supply air duct 75 to supply salt-free, dehumidified supply air ZL (UL).

To meet the different requirements in summer and winter operation, the outside air dehumidification heat pump has a second condenser, which in the outside air supply air flow AL / ZL after exiting the plate heat exchanger 51 is arranged. 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 Entwärmungsleistung for heat dissipation in the aggregate module 15 arranged electrical and electronic units 16 in conjunction with the respective for the aggregate module 15 specified limit of the temperature with the most favorable effect.

Due to the controllability of the circulating air fan 56 Thus, there is the possibility of temperature control by by regulating the means of the circulating air fan 56 recirculated circulating air UL a continuous adjustment of the required circulating air UL and thus the circulation of suitable air quantities takes place.

By variable amounts of air both the outside air AL to supply air ZL and the circulating air UL can 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 as well as in the aggregate module 15 required cooling power and an emergency heating at standstill of the wind power plant are significantly affected. In particular, with a setting of 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.

• 1. da die im Aggregatemodul 15 angeordneten Wärme abgebenden elektrischen und elektronischen Aggregaten 16 im Sommer eine hohe Wärmeleistung abgeben, wo bei die Turmwandungen in dieser Zeit nur einen geringen Kühleffekt haben, wird der festgelegte, individuelle Grenzwert der Lufttemperatur im Aggregatemodul 15 erreicht, so dass es günstiger ist, die Energie aus dem Entfeuchtungswärmepumpenprozess (Reheat) der Außenluft AL beziehungsweise Zuluft ZL nach dem Austritt aus dem Plattenwärmetauscher 51 zuzuführen, da bei einer Übertragung der Energie (Reheat) vor Eintritt in den Plattenwärmetauscher 51 auch eine Energieübertragung auf den Abluftstrom Ab(UL) der Umluft UL stattfinden würde. Die Temperatur des Zuluftstromes ZL(UL) der Umluft UL wäre dann zu hoch und könnte die im Aggregatemodul 15 angeordneten elektrischen und elektronischen Aggregate 16 nicht ausreichend kühlen.
• 2. bei einer Anordnung nach dem Plattenwärmetauscher 51 bewirkt der Entfeuchtungsprozess in der Außenluft-Zuluft AL/ZL gleichzeitig eine Temperaturabsenkung, die im Energieaustausch des Plattenwärmetauschers 51 eine reduzierende Wirkung auf die Temperatur des Abluftstromes Ab(UL) der Umluft UL und damit auf die Entwärmungsleistung im Aggregatemodul 15 hat.
• 3. da die Wärmeübertragung des Plattenwärmetauschers 51 von der Temperaturdifferenz bestimmt wird, ist der erste Kondensator vorzugsweise im Winter zu nutzen, während der zweite Kondensator vorzugsweise im Sommer genutzt wird. In Abhängigkeit von den jeweiligen Temperaturanforderungen können beide Kondensatoren auch im Teillastbetrieb gefahren werden, wozu beide Kondensatoren stufenlos mit wechselseitigen, variablen Teilleistungen automatisch geregelt werden.

Switching between the two capacitors of the fresh air dehumidification heat pump fulfills the following tasks:

• 1. there in the aggregate module 15 arranged heat-emitting electrical and electronic units 16 Delivering a high thermal output in summer, where the tower walls have only a slight cooling effect during this time, the set, individual limit value of the air temperature in the aggregate module 15 achieved so that it is cheaper, the energy from the dehumidification heat pumping process (reheat) of the outside air AL or supply air ZL after exiting the plate heat exchanger 51 to be supplied, as in a transfer of energy (reheat) before entering the plate heat exchanger 51 an energy transfer to the exhaust air flow Ab (UL) of the circulating air UL would take place. The temperature of the supply air flow ZL (UL) of the circulating air UL would then be too high and could be in the aggregate module 15 arranged electrical and electronic units 16 not cool enough.
• 2. in an arrangement after the plate heat exchanger 51 At the same time, the dehumidification process in the fresh air supply air AL / ZL causes a reduction in temperature, which results in the energy exchange of the plate heat exchanger 51 a reducing effect on the temperature of the exhaust air flow Ab (UL) of the recirculating air UL and thus on the heat dissipation in the aggregate module 15 Has.
• 3. since the heat transfer of the plate heat exchanger 51 is determined by the temperature difference, the first capacitor is preferably to use in winter, while the second capacitor is preferably used in the summer. Depending on the respective temperature requirements, both capacitors can also be operated in partial load operation, for which purpose both capacitors are steplessly regulated automatically with alternating, variable partial powers.

At standstill of the wind energy plant realizes the optimized air treatment system 6 an emergency operation, which is given for example in light wind, storm or accident or during maintenance of the wind turbine. For example, studies on the basis of wind and weather data for Heligoland have shown that a wind turbine is not in operation for more than 2000 hours per year due to weak winds or strong winds. In emergency operation, 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. However, in many cases the power network only provides limited energy and, in general, no waste heat for heating the systems and facilities of the wind power plant.

Particularly in strong winds and storms, saline, moist outside air AL from the vicinity of the wind energy plant in particular due to leaks in the nacelle 11 the wind turbine in the tower 10 and thus also in the aggregate module 15 is pressed, it is necessary to the overpressure inside the tower 10 and the gondola 11 to maintain. For this reason, the conventional air treatment device 2 with the positive pressure generating outside air fan 25 kept in operation and by means of the optimized air treatment system 6 In addition, it is ensured that the sucked moist and saline outside air AL is dehumidified and desalinated as completely as possible by filtering.

• – da die Heizeinrichtungen 58, 65 nicht aus der Abwärme der elektrischen oder elektronischen Aggregate 16 gespeist werden können, ergibt sich bei den über den Plattenwärmetauscher 51 geführten Umluft- und Außenluft-Zuluft-Strömen kein brauchbarer Energieaustausch, da keine Wärmeübertragung stattfindet;
• – der Umluftventilator 56 steht still und fördert keine Umluft, so dass keine Umluftströmung durch das Aggregatemodul 15 fließt;
• – die Außenluft-Entfeuchtungswärmepumpe ist in Betrieb, kühlt, entfeuchtet und heizt den Außenluftstrom AL auf, kann aber nicht bei jeder Wettersituation die 40%-Feuchte-linie erreichen;
• – zur Sicherheit und zur restlichen Nachheizung mit geringfügigem Energieeinsatz ist vorzugsweise ein Elektro-Heizregister mit Einspeisung aus dem Versorgungsnetz eingeschaltet und bewirkt eine Erhöhung der Temperatur des Zuluftstromes, so dass die Feuchtkennlinie von 40% erreicht wird und das kristallisierte Salz durch das Hochleistungsfilter 57 im Zuluftstrom abgeschieden werden kann.
• – auf dem Weg zum oberen Teil des Turmes 10 gibt der über den Zuluftkanal 74 geführte Zuluftstrom ZL einen geringen Anteil der Luftmenge über den Bypass 70 an das Aggregatemodul 15 zur Überdruckhaltung und zur Reduzierung des Feuchtegehaltes der Umluft ab. Zu diesem Zweck wird die Bypassklappe 700 (21 bis 23) geöffnet und auf eine bestimmte, üblicherweise geringe Luftmenge eingeregelt. Die Bypassluftmenge kann vorzugsweise auch über die Abluft des Umluftstromes in das Aggregatemodul 15 eingebracht werden, nämlich über die Verbindung zwischen dem Bypass und der Abluft der Umluft gemäß den 21 bis 23.

The optimized air treatment system according to the invention 6 works in emergency mode in principle as described above in normal operation, but with the following special features, since energy is only limited available:

• - because the heaters 58 . 65 not from the waste heat of electrical or electronic units 16 can be fed, results from the above the plate heat exchanger 51 guided Umluft- and fresh air supply air streams no useful energy exchange, since no heat transfer takes place;
• - the circulating air fan 56 stands still and does not promote circulating air, so that no circulating air flow through the aggregate module 15 flows;
• - The fresh air dehumidification heat pump is in operation, cools, dehumidifies and heats the outside air flow AL, but can not reach the 40% moisture line in any 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 flow, so that the wetness of 40% is achieved and the crystallized salt by the high-level weighting filters 57 can be deposited in the supply air.
• - on the way to the upper part of the tower 10 gives the over the supply air duct 74 guided supply air flow ZL a small proportion of the air flow through the bypass 70 to the aggregate module 15 for overpressure maintenance and for reducing the moisture content of the circulating air. For this purpose, the bypass flap 700 ( 21 to 23 ) and adjusted to a certain, usually small amount of air. The bypass air quantity can preferably also via the exhaust air of the circulating air flow in the aggregate module 15 be introduced, namely on the connection between the bypass and the exhaust air of the circulating air according to the 21 to 23 ,

Due to the above measures, neither in the aggregate module 15 , still in the tower 10 or in the gondola 11 Condensation of the supply air ZL or circulating air UL occur.

As stated above, the evaporator 53 the outdoor air dehumidification heat pump, but also the evaporator 62 the circulating air dehumidification heat pump is equipped with a defrosting function for a partial load operation. For the de-icing function, 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. For the purpose of deicing the butterfly valves can optionally be opened or closed alternately, with both butterfly valves are open in normal operation, so that one half of the evaporator makes the cooling and / or dehumidification and the other half is de-iced with hot gas injection closed butterfly valve.

These Special function is additional then used when in part-load operation of the outside air volume flow considerably is lowered, resulting in incomplete evaporation of the refrigerant the dehumidification heat pump to lead can, so the risk of liquid leakage on the suction line, which by liquid blows to destroy the Run compressor would. In partial load operation, a refrigeration cycle is thus not in operation and a butterfly valve is closed so that the reduced Air flow only over the subarea of the Evaporator flows and thus ensures that the refrigerant evaporates completely and liquid shocks avoided become.

in the relationship to the big one Tower cross section and the big one tower height as well as due to the large Air volume is the usual amount of fresh air introduced into the tower rather than low. The flow behavior and that too associated cooling behavior Special attention should therefore be paid in the tower.

If the amount of fresh air - even with respect to the heating - at low speed in the tower 10 introduced, so the flow is driven in particular by the thermal, as warmer air is known to rise. Due to the large tower height and the large tower diameter, the temperature of the air stream, which is the nacelle 11 achieved, but not controlled. Due to temperature stratifications, so-called layers are formed along the route and, due to different temperatures of the tower wall, which prevail, for example, on the north side and on the south side with and without solar radiation, unwanted secondary currents develop. Thus, for example, the faster cooling air on the cooler side of the tower, for example the north side or cold wind side, which is not irradiated by the sun, quickly develop into a falling air flow, which is associated with the formation of undesirable condensation phenomena.

To avoid this, the in 28 illustrated embodiment of a device for aftertreatment, supplementary air treatment and targeted air flow of the different air streams in addition to the Nachheizregister or heat exchanger 8th according to 10 a jet nozzle 80 for blowing the supply air flow ZL in the entrance of the tower 10 at high speed, which is advantageously located in the center of the tower diameter. As a result, in the simple air treatment device 3 , the improved air treatment device 4 or optimal air treatment device 5 and optionally in the heat exchanger 8th heated supply air flow ZL targeted to the top of the tower 10 and closer to the gondola 11 be introduced.

The air jet ZL '''at high speed induced on its flow permanently air standing LS from all sides of the tower 10 , where air stratification and temperature stratifications are torn open and secondary flows are avoided.

The most centric arrangement of the jet nozzle 80 avoids distracting and leaning the flow to the tower wall and thus the so-called Coanda effect.

to Air introduction will be a nozzle or diffuser shape, because while the static pressure losses are kept low.

In 28 are the outside air AL, the free supply air flow ZL '''in the tower 10 , the exhaust FL from the gondola 11 , the conventional Luftaufbereitungsge advises 2 for pre-desalination and pre-dehumidification and the optimal air treatment facility 5 for air conditioning with plate heat exchanger and dehumidification heat pump, the supply air overpressure air duct in the supply air duct 74 through the aggregate module 15 , and the recirculating air UL for targeted extraction, possibly with duct system and possibly with volumetric flow controllers and for targeted supply of fresh air with duct system and possibly with volumetric flow controllers, as well as an optional heat exchanger 8th for heating the supply air ZL '''in the tower 10 and the gondola 11 shown.

Based on the in 29 illustrated Mollier-h, x diagram will be the effect of the optimized air treatment system 6 explained with the optimal air treatment device.

Based on an outside air with a temperature of about 7 ° C at 100% relative humidity at point P1 is according to the arrow A, the sucked outside air through the evaporator 53 while cooled to about 4 ° C at a constant relative humidity. In the plate heat exchanger 51 according to the 4 to 7 is the cooled down outside air in the plate heat exchanger 51 by means of the recirculation mode in the unit module 15 recorded by the electrical and electronic units 16 heated heat according to the arrow B of 4 ° C to about 21 ° C at a relative humidity of 30%. By the subsequent heating or reheating in the condenser 55 the dehumidification heat pump, the supply air is heated according to the arrow C to about 27 ° C and as supply air flow through the supply air duct 6 in the upper part of the tower 10 , ie, outside the aggregate module 15 in the interior of the tower 10 and the gondola above 11 blown. Until reaching the outlet openings 3 the injected supply air is cooled down to a maximum temperature of 7 ° C at a maximum of 80% relative humidity according to the arrow D, which ensures that the dew point can not be reached and condensation can not occur.

At the same time, the air is recirculated by the unit module 15 guided circulating air according to the point P2 according to 29 according to the arrow E as exhaust air return air to the plate heat exchanger 51 supplied with a temperature of 30 ° C and a relative Feuch te of 40% and in the plate heat exchanger 51 with hermetically separated from the outside air / supply air and overpressure flow guide through the plate heat exchanger 51 cooled to about 15 ° C with increase in relative humidity to about 100% and the recirculation / supply air opening of the aftertreatment device 5 to the aggregate module 15 issued.

The arrow F denotes the direction of action of the partial pressure, the 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 effected as described above.

The Line G highlights the line of 80% relative humidity.

• 1. Führung der aus der Umgebung angesaugten Außenluft durch einen Luftführungskanal 6 durch das Aggregatemodul 15 hindurch zu dem oberhalb des Aggregatemoduls 15 liegenden Teil des Turmes 10 und zu der an dessen Spitze befindlichen Gondel 11, so dass die im Aggregatemodul 15 angeordneten elektrischen und elektronischen Aggregate 16 nicht mit salzhaltiger Luft in Berührung kommen und daher keine Kontamination der Aggregate 16 erfolgt.
• 2. Führung der Außenluft durch einen ersten Strömungsweg des Nachbehandlungsgerätes 5 mit einem Plattenwärmetauscher 51 getrennt von einem zweiten Strömungsweg zur Führung eines Umluftstromes durch das Aggregatemodul 15 über Zuluft- und Abluftkanäle 75, 76 mit einer hermetischen Trennung der Luftströme bei gleichzeitiger indirekter Energieübertragung – zum Zwecke der Kühlung der durch das Aggregatemodul 15 geführten Umluft, – zum Zwecke der Erwärmung in den Turm 10 und die Gondel 11 eingeblasenen Zuluft; – zum Zwecke der Entfeuchtung des Umluftstromes bei entsprechenden Temperaturdifferenzen.
• 3. Ein integriertes Entfeuchtungswärmepumpensystem dient der Feuchtereduzierung der Außenluft und deren gleichzeitiger Aufheizung mit der Gesamtwirkung, dass nach Abkühlung der Außenluft im Turm 10 der Taupunkt nicht erreicht wird bzw. nicht erreicht werden kann, so dass eine Kondensation im Turm 10 und in der Gondel 11 vermieden wird.
• 4. Gezielte Zu- und Rückluftführung nach dem Umluftprinzip im Aggregatemodul 15 durch Luftführungskanäle 7, 8, die ggf. mit zusätzlichen Volumenstromreglern in den einzelnen Zonen bzw. Etagen des Aggregatemoduls 15 zur optimalen Luftreinigung und zur gezielten Erwärmung der elektrischen und elektronischen Aggregate 16 versehen werden, deren Wärme über die Oberflächen der elektrischen und elektronischen Aggregate 16 abgegeben wird.
• 5. Ergänzende Nachheizung der Zuluft, vorzugsweise unter Einbeziehung einer Regeleinrichtung, zum Turm 10 und der Gondel 11 aus der Abwärme der elektrischen und elektronischen Aggregate 16 zur Vermeidung einer Kondensation im Turm 10 und in der Gondel 11.
• 6. Anordnung eines Hochleistungs-Feinfilters 61 zur weiteren Reduzierung des Salzgehaltes der durch das Aggregatemodul 15 geführten Umluft bei Feuchtewerten von weniger als 40% relativer Feuchte.
• 7. Optionale Entfeuchtungswärmepumpen-Umschaltung mit einem zusätzlichen Kondensator auf Umluft zur Notbeheizung insbesondere im Winterbetrieb und/oder bei stillgelegter Windenergieanlage.

The method according to the invention and the device according to the invention for air treatment in wind power plants, in particular in offshore wind power plants, collectively achieve the following effects and advantages:

• 1. Guide the sucked from the outside air through an air duct 6 through the aggregate module 15 through to the above the aggregate module 15 lying part of the tower 10 and to the gondola at the top 11 so that in the aggregate module 15 arranged electrical and electronic units 16 do not come in contact with salty air and therefore no contamination of the aggregates 16 he follows.
• 2. Guiding the outside air through a first flow path of the aftertreatment device 5 with a plate heat exchanger 51 separated from a second flow path for guiding a circulating air flow through the aggregate module 15 via supply air and exhaust air ducts 75 . 76 with a hermetic separation of the air streams with simultaneous indirect energy transfer - for the purpose of cooling by the aggregate module 15 guided circulating air, - for the purpose of heating in the tower 10 and the gondola 11 blown supply air; - For the purpose of dehumidifying the circulating air flow at appropriate temperature differences.
• 3. An integrated dehumidification heat pump system is used to reduce the humidity of 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 reached, allowing a condensation in the tower 10 and in the gondola 11 is avoided.
• 4. Targeted supply and return air ducts according to the recirculation principle in the unit module 15 through air ducts 7 . 8th , if necessary, with additional volume flow controllers in the individual zones or floors of the unit module 15 For optimum air purification and targeted heating of electrical and electronic units 16 be provided whose heat over the surfaces of the electrical and electronic units 16 is delivered.
• 5. Supplementary reheating of the supply air, preferably with the involvement of a control device to the tower 10 and the gondola 11 from the waste heat of the electrical and electronic aggregates th 16 to avoid condensation in the tower 10 and in the gondola 11 ,
• 6. Arrangement of a high-performance fine filter 61 to further reduce the salt content of the aggregate module 15 guided recirculation at humidity values of less than 40% relative humidity.
• 7. 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.

Depending on the design of a wind turbine and depending on the tower height of the wind turbine are above the unit module 15 further intermediate decks, ie separations in the cross section of the tower 10 , intended. This will be the inside of the tower 10 by means of the outside air fan 25 injected induction jet of the supply air guide on the way to the nacelle 11 interrupted or obstructed on its flow path. By such intermediate decks, the supply air stream slows down by permanent induction, ie beam thickening, so that it is recommended for large tower heights to accelerate the dynamics of the supply air flow. In addition, the heated supply air flow, which also by the thermal effect upwards in the direction of the nacelle cools 11 is driven, on the long way to the gondola 11 on the tower walls, so that the thermal buoyancy gradually slows down.

on the other hand Tween decks offer a good opportunity, especially for larger tower heights to maintain or increase the dynamics of the supply air stream by a preferably centric arranged, the speed of supply air increasing Device such as a nozzle or a diffuser the flow rate the supply air is increased selectively and a directed flow with high induction behavior above each intermediate deck generated again. This arrangement can be repeated for each intermediate deck with the speed increasing device being designed that will be the beam length the height of the next intermediate decks reached and there from the next speed-increasing device recorded and continued becomes.

This technical solution with an arrangement designed as a nozzle or diffuser speed-increasing device is as long as without a mechanical auxiliary unit, such as a fan, off, as long as an intermediate deck represents an airtight foreclosure and by the central outdoor fan 25 introduced air quantity due to the significant overpressure behavior can only flow through the nozzle or the diffuser of the speed increasing device and the intermediate deck has no bypasses in the form of leaks. In this case, the outside air fan is able to generate a sufficient overpressure, up to the nacelle 11 the wind energy plant is sufficient so that the required speed increase can be effected via the built-in nozzles or diffusers or comparable devices.

However, the Tween Deck rejects according to the 30 and 31 On its side edges to the tower wall gap distances or openings in the intermediate deck are provided for carrying out an elevator car or other facilities, as are 30 mechanical accessories such as fans 80 . 81 . 82 required in order to increase the dynamic speed of the supply air flow ZL, ZL ', ZL'',ZL''', since the introduced via the outside air fan air quantity due to the large pressure behavior penetrates all openings, resulting in an uncontrolled flow behavior in the tower 10 as well as the gondola 11 can develop.

31 shows the generation of a propulsion jet formed from the primary air and secondary air flows formed by induction and in the region of the intermediate deck above the aggregate module 15 occurring at the edge regions of the intermediate deck bypass flows according to the in 31 registered arrows.

In order to achieve a targeted flow of Zuluftstromes and avoid bypass flows through the marginal gaps or elevator bushings, it is advantageous to the fans 80 . 81 . 82 that the flow in the centric area of the tower 10 generate again, with a slightly increased, suitable amount of air, for example, + 10%, compared to the supply air interpreted, 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 currents from the overpressure behavior of the outside air fan 25 arise.

The mechanical air conveyors in the form of additional fans 80 . 81 . 82 are designed with a very low static pressure, because the outside air fan 25 Generates a significant overpressure, only after the entire way through the tower 10 finally in the gondola 11 can flow out and 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 pressure until the entrance to the nacelle 11 preserved.

32 shows the optimized air treatment system 6 for the in 30 illustrated wind energy plant in conjunction with the conventional air treatment or desalination device 2 for pre-dehumidification and desalination of the outside air AL.

Due to the cooling effect by the tower walls in conjunction with the long flow paths, it turns out according to 33 as advantageous, in conjunction with the mechanical air conveyor 80 . 81 . 82 the cooled on sections air flow through heaters 8th . 83 . 84 , for example, from the waste heat in the aggregate module 15 arranged, heat-emitting electrical and electronic units 16 is fed again to heat up. The temperatures throughout the tower 10 can be made more uniform compared to a single central heating and the temperature-condensation behavior in the tower 10 favorably influence.

The arrangement of a high-performance filter and a heat exchanger or an additional heating device in the optimal air treatment device 5 can also according to 34 in the area of a nozzle with fan 80 above the aggregate module 15 with the high performance filter 59 and the heat exchanger 8th be relocated or additionally arranged.

The solution according to the invention has been described above using the example of an offshore wind power plant with the climatic conditions prevailing in the seawater region of a humid and salty outside air during seasonally very cold or very warm outside air temperatures. This results in the requirements of dehumidification and desalination of the outside air as well as providing a dehumidified and desalinated supply air in the area of the unit module 15 , inside the tower 10 and in the gondola 11 to prevent corrosion and to ensure the dissipation of heat loads in the unit module. However, 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.

Independent of other, harsh environments is dehumidification and the associated safety against condensation even in land-based wind turbines a significant point, because wind turbines have electrical and electronic devices that are both sensitive to excessive Moisture values at which they are exposed to increased corrosion are, as well as inadmissible high temperatures react, leading to destruction of the electrical and electronic Facilities lead can.

In Modification of the embodiments described above must be in such wind power plants not all facilities immediately can be arranged in the tower, but can also be in containers or buildings next to the tower of the wind energy plant be provided. Even at such outbuildings or containers is the Dehumidification of the outside air or the avoidance of condensation and optionally the heat removal of the electrical and electronic units of considerable Importance.

1

Offshore Wind energy plant

2

Air handling or desalination device

3

easy Air treatment device

4

improved Air treatment device

5

optimal Air treatment device

6

optimized Air treatment system

8th

heater

10

tower

11

gondola

12

rotor blades

13

outflow openings

14

Air inlet opening

15

module of units

16

electrical and electronic components and aggregates

21

first Droplet

22 23

coalescence

24

second Droplet

25

Fresh air or overpressure fan

31

heater or air heater

32

High efficiency filter

41

Evaporator

42

compressor

43

capacitor or reheat coil

44

High efficiency filter

50

casing

51

Air treatment device with recuperative Heat recovery system (plate heat exchanger)

52

bypass dampers

53

Evaporator or cooler

54

compressor

55

capacitor or Reheat Registry

56

circulation fan

57

High efficiency filter in the outside air supply air flow

58

heater

59

second capacitor

60

bypass

61

High efficiency filter in the circulating air stream

62

Evaporator or cooler

63

compressor

64

capacitor or reheat register

65

heater

66

second Capacitor / Reheat register

70 71, 72

bypass

74

supply air duct

75, 76

Forced-air ducts

80

Jet nozzle

81, 82

fans

83 84

heaters

700

bypass damper

701 702

bypass

711 712

bypass dampers

713

bypass line

721 722

bypass dampers

723

bypass line

AL

outside air

ZL

supply air

FL

Exhaust air

UL

circulating air

From (UL)

exhaust the circulating air

ZL (UL)

supply air the circulating air

Claims (41)

Process for air treatment in wind energy installations, in particular in offshore wind energy installations, with a tower ( 10 ), at the upper end of which a gondola ( 11 ) with a generator and at least one rotor blade ( 12 ) and in its interior heat-dissipating electrical and electronic units ( 16 ) such as switchgear, switching devices, transformers, frequency converters and the like in an aggregate module ( 15 ) of the tower ( 10 ) are arranged and the at least one air inlet opening ( 14 ) and an air outlet opening ( 13 ), wherein via the air inlet opening ( 14 ) from the surroundings of the tower ( 10 ) moist and salty outside air (AL) is sucked, characterized in that via the air inlet opening ( 14 ) from the surroundings of the tower ( 10 ) sucked moist and salty outside air (AL) is heated until a predetermined relative humidity of the outside air (AL) is reached, in which the outdoor air (AL) Salzaerosole are at least partially crystallized, that the crystallized Salzaerosole and in the outside air (AL Salt particles are deposited and that the dehumidified and desalinated outside air (AL) as supply air (ZL) to the interior of the tower ( 10 ) and / or to the aggregate module ( 15 ) is delivered. A method according to claim 1, characterized in that via the air inlet opening ( 14 ) from the surroundings of the tower ( 10 ) sucked in moist and salty outside air (AL) in an air treatment device ( 4 ) and thereby reducing the absolute humidity of the outside air (AL), that the cooled and dehumidified outside air (AL) is heated until a predetermined relative humidity of the outside air (AL) is reached, at which the salt aerosols contained in the outside air (AL) at least partially crystallized, that the crystallized salt aerosols and in the outside air (AL) contained salt particles are deposited and that the dehumidified and desalinated outside air (AL) as supply air (ZL) to the interior of the tower ( 10 ) and / or to the aggregate module ( 15 ) is delivered. Method according to at least one of the preceding Claims, characterized in that the cooled and dehumidified outside air (AL) heated becomes less than or equal to the relative humidity of the outside air (AL) 40% is. Method according to at least one of the preceding Claims, characterized in that the heated outside air (AL) is filtered and the crystallized salzaerosols and salt particles contained in the outside air (AL) be deposited. Method according to at least one of the preceding claims, characterized in that via the air inlet opening ( 14 ) from the surroundings of the tower ( 10 ) sucked in moist and salty outside air (AL) or the cooled and dehumidified outside air (AL) with energy from the waste heat of heat-emitting electrical and electronic units ( 16 ) is heated. A method according to claim 5, characterized in that via the air inlet opening ( 14 ) from the surroundings of the tower ( 10 ) sucked in moist and salty outside air (AL) or the cooled and dehumidified outside air (AL) of an air treatment device ( 5 ) is supplied with separate flow paths, in which a recirculating air flow (UL) which is in heat exchanging connection with the outside air (AL) is circulated in a closed circuit through the aggregate module (FIG. 15 ) and by the heat emission of the electrical and electronic units ( 16 ) dissipates absorbed heat energy to the outside air (AL), of which, excluding the aggregate module ( 15 ) heated supply air (ZL) with overpressure to the interior of the tower ( 10 ) and the gondola ( 11 ) is delivered. A method according to claim 6, characterized in that the volume flow of the outside air (AL) and / or the circulating air (UL) are generated independently of each other and for adjusting the heat transfer in the aggregate module ( 15 ) and / or the temperature or humidity of the supply air (ZL) are controlled and regulated. A method according to claim 6 or 7, characterized characterized in that the outside air (AL) via a dehumidification heat pump ( 41 - 44 ; 53 - 55 . 59 ) with an outside air stream (AL) arranged evaporator ( 41 ; 53 ), Compressor ( 42 ; 54 ), Condenser or Reheatcoil ( 43 ; 55 ) and high performance filters ( 44 ; 59 ) to be led. Method according to at least one of the preceding claims 6 to 8, characterized in that the air treatment device ( 5 ) an air treatment unit with heat recovery ( 51 ), through which the hermetically separated flow paths of the outside air supply air flow (AL / ZL) and the circulating air flow (UL) are guided, that the dehumidification heat pump ( 53 - 55 ; 59 ; 63 ) at least one capacitor or rehab register ( 55 . 63 ), which in the flow direction of the outside air supply air flow (AL / ZL) before the air treatment unit with heat recovery ( 51 ) and / or in the flow direction of the outside air supply air flow (AL / ZL) after the air treatment unit with heat recovery ( 51 ) is arranged. A method according to claim 9, characterized in that the dehumidification heat pump ( 53 - 55 ; 59 ; 63 ) two capacitors or reheat registers ( 55 . 63 ), of which a first capacitor ( 55 ) in the flow direction of the outside air supply air flow (AL / ZL) before the air treatment unit with heat recovery ( 51 ) and the second capacitor ( 63 ) in the flow direction of the outside air supply air flow (AL / ZL) after the air treatment unit with heat recovery ( 51 ), and that by switching from the first capacitor ( 55 ) to the second capacitor ( 63 ) or by stepwise connection of the second capacitor ( 63 ) to the first capacitor ( 55 ) the supply air flow (ZL) is further heated. A method according to claim 9 or 10, characterized in that the proportion of the by the air treatment unit with heat recovery ( 51 ) guided outside air supply air flow in response to a temperature and / or humidity control of the optimized air treatment system ( 6 ) is set. Method according to at least one of the preceding claims 6 to 11, characterized by a condenser arranged in the circulating-air flow path (UL) ( 62 ), to which heating demand in the aggregate module ( 15 ) is switched. Method according to at least one of the preceding claims, characterized by a bypass ( 70 ) from the supply air flow (ZL) to the recirculating air flow (UL) between that from the evaporator or cooler ( 62 ), Condenser or reheat register ( 64 ), Compressor ( 63 ) and high performance filters ( 61 ) formed Entfeuchtungswärmepumpensystem in the recirculating air flow (UL) for overpressure in the circulating air flow (UL). A method according to claim 13, characterized in that a flap system ( 640 . 700 ) connects or bypasses the bypass via a humidity measurement. Method according to at least one of the preceding claims, characterized in that that of the air treatment device ( 5 ) supply air stream (ZL) via a heat exchange device ( 8th ) resulting from the waste heat of the electrical and electronic units ( 16 ) absorbed heat energy to the supply air flow (ZL) as a function of the air temperature in the interior of the tower ( 10 ) and the gondola ( 11 ). Method according to at least one of the preceding claims 6 to 14, characterized in that the supply air (ZL) at least in the section between the air treatment device ( 5 ) and the entrance to the interior of the tower ( 10 ) in a supply air duct ( 74 ) to be led. Method according to at least one of the preceding claims, characterized in that that of the air treatment device ( 5 ) additionally dehumidified supply air (ZL) and with the energy obtained from the dehumidification process before delivery to the interior of the tower ( 10 ) is heated. Method according to at least one of the preceding claims 6 to 11, characterized in that the supply air (ZL) at high speed and preferably in the center of the tower diameter in the interior ( 100 ) of the tower ( 10 ) is blown. Method according to at least one of the preceding claims, characterized in that via the air inlet opening ( 14 ) from the surroundings of the tower ( 10 ) sucked moist and salty outside air ( 1 ) via a mist eliminator 41 for coarse pre-separation of rain, spray is passed. Method according to at least one of the preceding claims, characterized in that the air treatment device ( 5 ) an air treatment device ( 2 ) for desalination of the outside air ( 1 ) and for generating an overpressure in the interior of the tower ( 10 ) downstream, which preferably has a first droplet separator ( 21 ) for coarse pre-separation of rain, spray and the like, a Koaleszenzabscheider ( 22 . 23 ) to form larger drops, a second drop separator ( 24 ) as Nachabscheider for intercepting and separating the previously formed droplets and the required air flow generating outside air fan ( 25 ) having. Apparatus for air treatment in wind energy installations, in particular in offshore wind energy installations, having a tower ( 10 ), at the upper end of which a gondola ( 11 ) with a generator and at least one rotor blade ( 12 ) and in its interior heat-dissipating electrical and electronic units ( 16 ) such as switchgear, switching devices, transformers, frequency converters and the like in an aggregate module ( 15 ) of the tower ( 10 ) are arranged and the at least one air inlet opening ( 14 ) and an air outlet opening ( 13 ), wherein via the air inlet opening ( 14 ) from the surroundings of the tower ( 10 moist and saline outside air (AL), characterized by an air treatment device ( 3 ) with a heating device or an air heater ( 31 ) for heating the outside air (AL) or in an air treatment or desalination device ( 2 ) desalinated and dehumidified outside air (AL ') and a high-performance filter ( 32 ) for filtering the salt aerosols crystallized to particles in the outside air (AL) or desalinated and dehumidified outside air (AL ') and for delivering heated supply air (ZL) via the aggregate module ( 15 ) in the tower ( 10 ) and in the gondola ( 11 ). Apparatus for air treatment in wind energy installations, in particular in offshore wind energy installations, having a tower ( 10 ), at the upper end of which a gondola ( 11 ) with a generator and at least one rotor blade ( 12 ) and in its interior heat-dissipating electrical and electronic units ( 16 ) such as switchgear, switching devices, transformers, frequency converters and the like in an aggregate module ( 15 ) of the tower ( 10 ) are arranged and the at least one air inlet opening ( 14 ) and an air outlet opening ( 13 ), wherein via the air inlet opening ( 14 ) from the surroundings of the tower ( 10 moist and saline outside air (AL), characterized by an air treatment device ( 4 ) with one from an evaporator ( 41 ) for reducing the absolute moisture content of the external air supplied (AL) or in an upstream air treatment or desalination ( 2 ) desalinated and dehumidified outside air (AL), a condenser or a reheat coil ( 43 ) for reheating the outside air (AL) to a relative humidity of less than or equal to 40% and a compressor ( 42 ) existing dehumidification heat pump, and with a high-performance filter ( 44 ) for salt separation. Apparatus for air treatment in wind energy installations, in particular in offshore wind energy installations, having a tower ( 10 ), at the upper end of which a gondola ( 11 ) with a generator and at least one rotor blade ( 12 ) and in its interior heat-dissipating electrical and electronic units ( 16 ) such as switchgear, switching devices, transformers, frequency converters and the like in an aggregate module ( 15 ) of the tower ( 10 ) are arranged and the at least one air inlet opening ( 14 ) and an air outlet opening ( 13 ), wherein via the air inlet opening ( 14 ) from the surroundings of the tower ( 10 moist and saline outside air (AL), characterized by an air treatment device ( 5 ) with an air treatment device ( 51 ) with recuperative heat recovery system and hermetically separated first and second flow paths, wherein the first flow path through the air inlet opening ( 14 ) sucked outside air (AL) to the at the interior of the tower ( 10 ) with the exception of the aggregate module ( 15 ) supplied supply air (ZL) and the second flow path in recirculation mode supply air to the unit module ( 15 ) and exhaust air or return air from the aggregate module ( 15 ) sucks. Apparatus according to claim 23, characterized in that the air treatment device with recuperative heat recovery system a plate heat exchanger ( 51 ), which in the flow direction of the first flow path to one with the air inlet opening ( 14 ) associated air treatment device ( 2 ) is arranged for desalination of the sucked outside air (AL). Device according to claim 24, characterized in that the plate heat exchanger ( 51 ) on the inlet side of the cooled outside air (AL ') adjustable bypass flaps ( 52 ) having. Device according to at least one of the preceding claims, characterized in that the outside air fan ( 25 ) on the suction side, in the flow direction of the outside air (AL) to the supply air (ZL) behind the air treatment device ( 3 . 4 . 5 ) is arranged. Device according to claims 23 to 26, characterized by a supply air duct ( 74 ) from the air treatment device ( 5 ) to that of the aggregate module ( 15 ) separate interior ( 100 ) of the tower ( 10 ). Apparatus according to claim 22, characterized in that the supply air duct ( 74 ) with a heat exchanger ( 8th ) connected to the electrical and electronic units ( 16 ) dissipates absorbed heat energy to the leading into the interior of the tower supply air flow of the first flow path. Apparatus according to claim 28, characterized in that the heat exchanger ( 8th ) at the supply air flow of heat energy as a function of the temperature in the interior of the tower ( 10 ) and / or the gondola ( 11 ) and that at least one of the temperature in the interior of the tower ( 10 ) and / or the gondola ( 11 ) detecting temperature sensor is connected to a control device. Device according to at least one of the preceding claims 23 to 29, characterized in that the circulating air (UL) in supply air and exhaust air ducts ( 75 . 76 ) to the aggregate module ( 15 ) and the aggregate module ( 15 ) to be led Device according to at least one of the preceding claims 23 to 30, characterized in that in the circulating air flow path (UL) another high-performance filter ( 61 ) is arranged. Apparatus according to claim 31, characterized in that the further high-performance filter ( 61 ) in a bypass ( 60 ) with two jalousie flaps ( 602 . 603 ) whose position as a function of a moisture measurement determine the proportion of the circulating air flow (UL), which is determined by the flow in the bypass channel ( 601 ) high performance filters ( 61 ). Device according to at least one of the preceding claims 23 to 32, characterized in that the circulating air fan 56 For continuous variable delivery of circulating air quantities has a regulated drive. Device according to at least one of the preceding claims 23 to 33, characterized in that both in the outside air supply air flow (AL-ZL) one from an evaporator or cooler ( 53 ), Condenser or reheat register ( 55 ) and compressor ( 54 ) existing Entfeuchtungswärmepumpensystem and in the recirculating air flow (UL) a from an evaporator or cooler ( 62 ), Condenser or reheat register ( 64 ) and compressor ( 63 ) existing and in the exhaust duct ( 76 ) of the recirculating air (UL) upstream of the high-performance filter ( 61 ) arranged dehumidifying heat pump system are arranged. Device according to at least one of the preceding claims 23 to 34, characterized by a supply air duct ( 74 ) and with the recirculation air flow path (UL) between the evaporator and radiator ( 62 ), Condenser or reheat register ( 64 ), Compressor ( 63 ) and the high-performance filter ( 61 ) formed Entfeuchtungswärmepumpensystem in the circulating air flow (UL) bypass ( 70 ) for overpressure maintenance in the recirculating air flow path (UL) Device according to at least one of the preceding claims 23 to 35, characterized in that in the supply air flow path (ZL) of the air treatment device ( 5 ) behind the plate heat exchanger ( 51 ) and before the high-performance filter ( 57 ) an independent heating device ( 58 ), preferably an electric heater, is arranged. Device according to at least one of the preceding claims 20 to 24, characterized by a bypass ( 71 ) in the flow path of the circulating air flow (UL) with controllable bypass flaps ( 711 . 712 ) and a bypass line ( 713 ) for passing the recirculating air flow (UL) to the high-performance filter ( 61 ) and a bypass ( 72 ) in the fresh air supply air flow path (AL / ZL) with controllable bypass flaps ( 721 . 722 ) and a bypass line ( 723 ) for passing the supply air flow (ZL) to the high-performance filter ( 59 ), whereby the bypass valves ( 711 . 712 respectively. 721 . 722 ) are independently controllable and are adjustable by a control device in such a position that the air flows at low humidity values either the high-performance filter ( 57 . 61 ) or via the bypass lines ( 713 . 723 ) on the high-performance filters 57 . 61 passed by Apparatus according to at least one of the preceding claims 23 to 37, characterized by additional dehumidification heat pump systems in the outside air supply air flow (AL-ZL) and recirculation air flow (UL), wherein in the flow path of the circulating air flow (UL) provided additional Entfeuchtungswärmepumpensystem before from the waste heat of the electric and electronic aggregates ( 16 ) in the aggregate module ( 15 ) powered heating device ( 65 ) and from an evaporator / cooler ( 62 ), Compressor ( 63 ), a first capacitor ( 64 ) and a second condenser / reheat register arranged in the outside air supply air flow (AL-ZL) ( 66 ), which corresponds to the first capacitor / rehab register ( 64 ) and is operable together with this or mutually, while the dehumidification heat pump system arranged in the outside air supply air flow path (AL-ZL) is supplied from an evaporator / cooler (US Pat. 53 ), Compressor ( 54 ), a first capacitor / reheat register ( 55 ) and / or a second capacitor / reheat register ( 59 ) exists with reciprocal operation. Device according to at least one of the preceding claims 21 to 38, characterized in that a Weitwurtdüse ( 80 ) for blowing a Zuluftstromes in the entrance of the tower ( 10 ) is arranged at high speed in the center of the tower diameter. Device according to at least one of the preceding claims 21 to 39, characterized by on intermediate decks of the tower ( 10 ) arranged mechanical air conveyors, esp special fans ( 80 . 81 . 82 ), to increase the dynamic velocity of the supply air flow (ZL, ZL ', ZL'',ZL'''). Apparatus according to claim 40, characterized in that the mechanical air conveying devices ( 80 . 81 . 82 ) with preferably from the waste heat in the aggregate module ( 15 ) arranged, heat-emitting electrical and electronic units ( 16 ) fed heating devices ( 8th . 83 . 84 ) are connected.