EP2326836A2

EP2326836A2 - Method and apparatus for the treatment of air in wind turbines

Info

Publication number: EP2326836A2
Application number: EP09781552A
Authority: EP
Inventors: Frank Buss
Original assignee: Individual
Current assignee: Individual
Priority date: 2008-08-06
Filing date: 2009-08-06
Publication date: 2011-06-01
Also published as: WO2010015674A2; DE102008053814A1; WO2010015674A3

Abstract

Disclosed are a method and an apparatus for treating air in offshore wind turbines comprising a tower, at the upper end of which a nacelle (11) that has a generator and at least one rotor blade (12) is arranged, and in the interior of which heat dissipating electric and electronic units (16), such as switchgear, switching devices, transformers, frequency converters, and the like, are arranged in a unit module (15) of the tower (10), and which has at least one air inlet and air outlets (3). Ambient air AL sucked in from the surroundings of the tower (10) via an air inlet is conducted via a first flow path (AL'-ZL) of an air treatment system (6) comprising an air treatment device (5) that has separate flow paths (AL'-ZL, UL). The second flow path (UL) that is in heat exchanging connection with the first flow path (AL'-ZL) is guided through the unit module (15) in a closed loop and transfers the thermal energy absorbed from the dissipated heat of the electric and electronic units (16) to the first flow path (AL'-ZL) via the air treatment device (5), and the first flow path (AL'-ZL) dissipates incoming air (ZL") that is heated without using the unit module (15) to the interior (100) of the tower (10) and the nacelle (11) at a pressure above atmospheric.

Description

Method and device for air treatment in wind power plants

description

The invention relates to a method and a device for air treatment in wind power plants, in particular in offshore wind power plants, according to the preamble of claims 1 and 28 to 30.

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

For cooling the heat-dissipating electrical and electronic units 16 is outside air AL via a generally below the unit module 15 arranged air inlet opening 14, for example, an opening in an access door in the tower 10, of an air treatment unit 2, the components are shown schematically in Fig. 2 and be described below, sucked, cleaned and discharged with positive pressure as supply air ZL to the interior of the tower 10 so that the introduced and largely purified supply air flow ZL flows through the aggregate module 15, the heat absorbed by the electrical and electronic components and aggregates 16 radiation and discharged via outlet openings 13 in the nacelle 1 1 as exhaust air FL to the environment. Due to the overpressure in the interior of the tower 10 prevents saline sea air from leaking into the interior of the tower 10 and the nacelle 11 and thus accelerates corrosion processes. It flows the partially desalinated air freely through the aggregate module 15 and the tower 10 to the nacelle 11 and there can escape through leaks by overpressure.

Fig. 2 shows a schematic representation of a conventional air treatment device 2 for desalination of the sea air and for generating an overpressure in the interior of the tower 10. In a first stage, the air treatment device 2, a first droplet 21 as a main separator for coarse pre-separation of rain, spray, etc. , In a second stage, coalescence separators 22, 23 designed as aerosol filters are provided, which bind aerosols and form larger droplets. In a third stage, a second droplet separator 24 follows as a post-separator, which intercepts and separates the previously formed droplets. The required air flow is generated by means of an outside air or overpressure fan 25.

The air conditioning system according to FIG. 2 provided in the offshore wind power plant 1 thus fulfills the following tasks:

1. with a purified air flow, the surface heat of the components in the tower 10 and in the nacelle 11 is removed;

2. the introduced sea air (outside air) is cleaned by the salt aerosols contained in the air to protect against the corrosion within the tower 10 of the offshore wind energy plant 1 in the unit module 15 arranged electrical and electronic units 16;

3. by overpressure of introduced into the tower 10 and the nacelle 1 1 and largely purified supply air ZL prevents sea air penetrates with a high salt content. In this case, the supply and overpressure fan 45 is operated as a function of the external wind speed pressure-dependent, with an overpressure of about 2000 Pa can be generated, so that even in strong winds, i. at wind speeds up to 56 m / sec, the introduced, mostly purified

Zuluft ZL essentially escape in the gondola 11 existing leaks 3 and escape through corresponding overpressure flaps, ie can flow to the outside, while the ingress of unpurified, salty sea air even in strong winds in the interior of the tower 10 and the nacelle 1 1 by the generated pressure is prevented. A disadvantage of this conventional air treatment in offshore wind energy systems 1 is that the treatment of the sea or outdoor air AL achieved by desalination, a strong reduction of the salt content, but a residual content of salt is permanently entered into the tower 10, in particular in the form of The aerosol dissolved in the outside air, which can not be filtered out by the droplet and Koaleszenzabscheidern the air treatment unit 2. 0.005 mg / m ³ is exceeded 100 times, so that the electrical and electronic units 16 are contaminated despite the air conditioning and after a relatively short time considerable corrosion of the electrical and electronic Aggre gate 16 takes place.

Salt has different states of aggregation depending on the moisture content. At 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.

The present invention has for its object to provide a method and an apparatus for air treatment in wind power plants and in particular in offshore wind energy systems, the elimination or reduction of the salt and moisture content and thus the risk of condensation (dew point below) of ensure the unit module and air discharged into the tower or nacelle with positive pressure.

This object is achieved by a method having the features of claim 1 and devices having the features of claims 28 to 30.

The solutions according to the invention ensure elimination or at least a considerable reduction of the salt and moisture content and thus reduction of the risk of condensation due to dew point undershooting of an outside or supply air supplied to the unit module and into the tower or the nacelle by an outside air fan with overpressure. Volume flow and thus the risk of corrosion in the Aggregate module arranged electrical and electronic units and the inner wall and the devices in the tower and in the nacelle.

This simple air treatment device assumes that by heating the outside air to a relative humidity of 40%, the salt aerosols crystallized to particles can be separated in a high-performance filter as salt particles. Although this is a significant reduction of the residual salt content and thus the risk of corrosion in the unit module and inside the tower and connected in the nacelle, but can not be ensured under all climatic conditions and year-round, that the air flow in the aggregate module and inside the tower and the nacelle is maintained in such a way that, on the one hand, the heat emitted by the electrical and electronic units heat is dissipated with sufficient certainty and on the other hand, a risk of corrosion inside the tower and the nacelle can be excluded.

In addition, it should be noted that the wind energy plant is not in operation for many years of the year, for example in storms, light winds, incidents and for maintenance purposes. In order to ensure the greatest possible safety during the course of the year in terms of overpressure, salt-free, temperature maintenance, air humidity and avoiding condensation of the supply air delivered to the unit module and into the tower and the nacelle, an emergency operation is required which is insufficiently ensured with this method can be.

A comparison with the prior art substantially improved air treatment system is therefore characterized in that the cooled via the air inlet opening from the environment of the tower sucked wet and salty outside air cooled in an air treatment device and thereby the absolute humidity of the outside air is lowered, that the cooled and dehumidified outside air heats is reached to a predetermined relative humidity of the outside air, in which the Saiz aerosols contained in the outside air are at least partially crystallized, that the crystallized salt aerosols and salt particles contained in the outside air are separated and that the dehumidified and desalinated outside air as supply air to the interior of the tower and / or delivered to the aggregate module.

By cooling the humid and salty outside air while at the same time reducing the absolute moisture content of the outside air and the subsequent aftermath. a moisture content of the treated outside air of less than or equal to 40% relative humidity is achieved, so that the salt aerosols still contained in the outside air can be crystallized and separated. After the dehumidification and desalination of the outside air, the supply air flows freely and without special air supply systems into or through the aggregate module and through the upper part of the tower to the nacelle. This ensures that the dehumidified and desalinated supply air even at total recooling to the temperature value of the outside air due to cooling on the way from the unit module to the nacelle at any point the low level of dew point, ie a relative humidity of 100%, can achieve what the Danger of condensation in the entire wind energy system and thus significantly reduces the risk of corrosion.

The over the prior art significantly improved air treatment system is optimized taking into account the expenditure on equipment and leads to a significant reduction or elimination of the risk of corrosion inside a wind energy plant.

Preferably, the moist and saline outside air drawn in via the air inlet opening from the surroundings of the tower is heated until a predetermined relative humidity of the outside air is achieved, at which the salt aerosols contained in the outside air are at least partially crystallized, the crystallized salt aerosols and salt particles contained in the outside air are separated and the dehumidified and desalinated outside air is indirectly, freely cooled and discharged as cooled supply air to the interior of the tower and / or to the aggregate module.

In this case, preferably for the indirect, free cooling of the supply air hermetically separated from the supply air, but in good heat-conducting contact with the supply air flow standing air flow from the outside air to the exhaust air is used.

In addition, with increased cooling demand, the indirectly, freely cooled supply air before delivery to the interior of the tower and / or to the unit module) can be further cooled down with a mechanical cooling device.

The importance of desalination and dehumidification of the air introduced into the tower and the nacelle of a wind power plant will be explained in more detail with reference to FIGS. 3 to 6. The mechanisms in which corrosion occurs and the corrosion protection measures derived from it are of high relevance, since corrosion damage in practice causes considerable costs. Of particular importance is the atmospheric corrosion, ie the corrosion by air at temperatures between about -20 ⁰ C and 70 ⁰ C, which occurs both in the free atmosphere and in rooms of all kinds. It is estimated that 80-90% of all corrosion damage is due to atmospheric corrosion. Temperature and humidity are the main parameters when atmospheric corrosion occurs and, in their interaction, form the basic components of the climate. Since electrochemical processes can take place only in the presence of an electrolyte, there is no or almost no corrosion at sufficiently dry air. However, corrosion occurs not only when a metal surface is visibly wet, but also without visible wetting. Decisive for corrosion without visible wetting is the level of relative humidity, ie the level of saturation of the air.

In the case of corrosion, the reaction rate and thus the corrosion rate are influenced by the temperature. Thereafter, the corrosion increases with increasing temperature, with decreasing temperature and comes to a standstill at very low temperatures. This behavior can be explained physically by the fact that with decreasing temperature, the absolute moisture content drops sharply, which is equivalent to the absence of the electrolyte. The illustrated in Fig. 3 Mollier h, x-diagram illustrates this correlation by taking the ratios at a temperature of 30 ⁰ C and a temperature of -13 ⁰ C are entered in the Mollier h, x-diagram. At a temperature of 30 ⁰ C, the air can absorb up to 27 g / kg of water along the line A, while at a temperature of -13 ⁰ C, the air corresponding to the line B absorbs only 1 g / kg. This behavior expresses the strength of the electrolyte.

4 shows the influence of the moisture film thickness on the corrosion rate and illustrates that the greatest corrosion rate is given at about 100 μm thickness, while at lower and higher thicknesses the corrosion rate is substantially lower.

An increase in moisture and salt content invariably leads to increased corrosion in all common engineering metals, metal coatings and laminations. According to Fig. 5, the corrosion is measurable up to about 65% relative humidity at a constant temperature, but very low. In contrast, special In the case of steel, corrosion immediately occurs when water is deposited on the metal surface as a result of a lowering of the temperature, or thin skins are formed on the metal by adsorption. Only from about 70% relative humidity, the corrosion is considerable and increases with even greater humidity almost linearly with the increase in moisture. The moisture above which the corrosion becomes noticeable is called "critical humidity." If the surface is roughened by rusting, the rusting proceeds even at about 50% relative humidity, since the surface condensation in this case is greater than at one smooth surface.

Fig. 6 shows the range of critical humidity, i. H. the range of 70 to 100% relative humidity in the Mollier-h, x-diagram. In order to assess the risk of corrosion at various locations, the temperature and humidity values of the locations concerned are entered as a so-called "weather bubble" in relation to the "critical humidity" area shown in FIG. From these representations in the Mollier-h, x diagram, a large number of annual hours are in the range of "critical humidity." In some areas, the local weather data is almost without exception in the "critical humidity" range. In addition, the electrolyte is extremely intensified by the high salt content in the air, for example, when the wind energy plant is located in the coastal area or "offshore." For this reason, the corrosion rate under the influence of the sea climate is significantly higher than in the interior For this purpose, the weather bubble of the island of Heligoland, which is shown in outline in Fig. 6, shows that 8,533 hours per year in the range of "critical humidity", ie in the range of 70-100% relative humidity.

Due to massive movements of air masses between high and low pressure areas, but also by regular cooling phases between day and night, there is a physical relationship with respect to the change in relative humidity. In addition, it comes with rapid temperature change often condensation phenomena. It can be observed that during the transition between day and night, the range of critical humidity is reached quickly. As soon as the sun is missing as a heat source and the air temperatures drop, the relative humidity drops to a low and therefore critical level.

Temperature and humidity changes are not only due to the weather, but also in the mechanical cooling of air by means of a condenser, evaporator and

Note compressor. Namely for air conditioning and Entwärmungszwecken Only the temperature change, with which excess heat can be dissipated, often overlooks the problematic zones of "critical air humidity." Especially in the cooling of electrical and electronic equipment, the consequences of corrosion are often not considered of heat-emitting electrical and electronic equipment on ever smaller areas require high cooling performance, which is met with a large temperature difference and consequent low Einblastemperaturen in the equipment rooms.

The use of so-called free cooling in seasons with low outdoor temperatures for the purpose of saving energy has significant dangers with respect to the critical humidity. Dangers of this kind can only be avoided if adequate dehumidification takes place through deeper latent cooling and subsequent controlled afterheating achieves temperature and humidity values which are outside the "critical humidity".

A further optimized air treatment system is characterized in that the moist and saline outside air drawn in via the air inlet opening from the environment of the tower is supplied to the cooled and dehumidified outside air to an air treatment device having separate flow paths in which a heat exchanging connection with the outside air is established Circulating air flow is guided in a closed circuit through the unit module and the thermal energy absorbed by the heat dissipation of the electrical and electronic units emits heat to the outside air, is discharged from the under exclusion of the aggregate module heated supply air with pressure to the interior of the tower and the nacelle.

The optimized air treatment system ensures efficient heat dissipation of the surface heat emission of the electrical and electronic units and a controlled temperature maintenance in the tower to the nacelle by controlled heat transfer with feed from the waste heat of the electrical and electronic units. As a result of the hermetically separated guidance of two air streams, it is achieved that the outside air, which is still contaminated with salt, no longer flows freely through the aggregate module and thus can not contaminate the electrical and electronic units. Preferably, the volume flow of the outside air and / or the circulating air are generated independently of each other and controlled and adjusted for adjusting the heat transfer in the unit module and / or the temperature or humidity of the supply air.

The control and regulation of the recirculated circulating air allows a stepless adjustment of the required circulating air and thus a circulation of suitable air quantities. By variable amounts of air both the outside air to the supply air and the recirculation depending on parameters such as outdoor air temperature, humidity and salt content of the outside air and depending on the required cooling power in the unit module and emergency heating at standstill of the wind energy plant, the air treatment can be significantly influenced. 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 in outdoor air supply air and recirculated air quantities in the lowered operation under appropriate weather conditions and lower heat loads in Aggregate module also saves energy costs.

In one embodiment, the air treatment device includes an air treatment unit with heat recovery, through which the hermetically separated flow paths of the outside air supply air flow and the circulating air flow are guided and arranged in the flow direction of the outside air supply air before and / or after the air treatment unit with heat recovery capacitor or reheat register a dehumidification heat pump containing an evaporator, the at least one condenser or reheat register, and a compressor.

Regardless 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 dehumidification, ie, the moisture reduction is met in the same way. The arrangement of the condenser of the dehumidification heat pump upstream of the air treatment unit with heat recovery with immediate reheating after cooling in the evaporator of the dehumidification heat pump reduces the cooling effect of the circulating air flow in the air treatment unit with heat recovery, since the outside air supply air was already heated in the condenser , which would be technically disadvantageous, but would not affect the functioning of the dehumidification heat pump. If the outside air supply air stream is additionally heated immediately after leaving the air treatment unit with heat recovery, ie after the heat released from the circulating air flow, with the energy from the dehumidification process via the condenser or the heat register, then an even more favorable, namely causes lower value of the relative humidity of the outside air supply air.

The arrangement of the evaporator and condenser is not necessarily required at the air inlet or air outlet of the plate heat exchanger, but can also be provided somewhere within the channel system of the blown into the tower supply air.

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

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 capacitor is preferably used in winter and the second capacitor preferably in summer. Depending on the respective requirements, both capacitors can be operated in partial load operation, whereby both capacitors are automatically controlled in mutual operation or with variable partial loads.

The proportion of the outside air supply air flow guided by the air treatment unit with heat recovery is preferably set as a function of a temperature and / or humidity control of the optimized air treatment system.

By adjusting the guided by the air treatment unit with heat recovery outside air supply air flow can influence the energy exchange and thus on the temperature and / or humidity behavior of the air treatment device are taken.

In a further embodiment, a condenser is arranged in the circulating-air flow path, to which the heater module in the unit module is switched.

By this embodiment, when the heating demand in the unit module, for example, in the winter months at low or too low temperatures and / or emergency operation at standstill of the offshore wind energy plant, from the dehumidifying heat pump formed from the evaporator or cooler, condenser or reheat register and compressor be switched in the outside air supply air from the condenser of the dehumidification heat pump to the condenser in the circulating air flow, so that the dehumidification heat pump in the outside air supply air flow AL / ZL heated to the power module module supply air circulating air of the second flow path. The energy for this heating operation is supplied by other offshore wind power plants operated in the network.

By means of a bypass from the supply air flow to the circulating air flow between the dehumidification heat pump formed in the circulating air flow from the evaporator or cooler, condenser or reheat register, to maintain the overpressure in the circulating air flow, it is ensured that the circulating air flowing through the aggregate module does not flow through other areas the wind turbine is contaminated with salty air, the required amount of bypass air is very small, the humidity content of the circulating air is not significantly affected and prevents negative currents from the area of the tower of the wind turbine or the air inlet opening can penetrate into the aggregate module.

Preferably, the supply air flow discharged from the air treatment device to the inside of the tower is guided via a heat exchange device which releases heat energy absorbed from the waste heat of the electrical and electronic units to the supply air flow as a function of the air temperature in the interior of the tower and the nacelle, the supply air at least in the section between the air treatment device and the entrance into the interior of the tower is guided in a supply air duct. The effect and positive consequences of the heat exchange device are that in order to avoid condensation within the tower and the nacelle, the air is heated so far through the heat exchange device, ie an increase in temperature is caused even by the cooling effect of the tower walls and a drop in temperature Supply air in the tower and the nacelle dew point is not reached.

The air treatment device not only causes dehumidification and desalination of the outside air discharged from the air treatment device, but also takes over the dehumidification of the unit module by a targeted air extraction from the individual floors or platforms of the unit module via circulating air exhaust air ducts and a targeted air supply via circulating air supply air ducts in the individual floors or platforms of the aggregate module.

In a further embodiment, the supply air discharged by the air treatment device is additionally dehumidified, heated with the energy obtained from the dehumidification process prior to delivery to the interior of the tower and injected into the interior of the tower at high speed and preferably in the center of the tower diameter.

Furthermore, the moist and saline outside air drawn in via the air inlet opening from the environment of the tower can be conducted via a mist eliminator for coarse pre-separation of rain, spray.

Preferably, the air treatment system according to the invention is downstream of an air treatment device for desalination of the outside air and for generating an overpressure in the interior of the tower, preferably a first droplet separator for coarse pre-separation of rain, spray and the like, a Koaleszenzabscheider to form larger droplets, a second droplet Having as Nachabscheider for intercepting and separating the previously formed droplets and the required air flow generating outside air or overpressure fan.

To ensure that in sub-areas of the wind energy plant, in which larger heat loads incurred, a sufficient cooling of aggregates takes place without the delivered to the interior of the tower and / or to the module module dehumidified and desalinated supply air even with re-cooling to the value of the Outdoor air reaches the dew point again and, through targeted dehumidification, reaches a maximum If the relative humidity is less than 60% relative humidity, indirect, free cooling of the circulating air can be carried out by means of an additional outside air flow which is hermetically separated from the recirculating air flow, but in good heat-conducting contact with the circulating air flow is.

To use the cooling effect of the powerful steel tower of the wind energy plant, the processed supply air is injected at a high speed obliquely upward, sharp on the tower wall upwards in the tower according to another process feature so that the injected air flow is moved along the tower wall and in the tower creates a rotational movement (vortex flow), which tears air layers and air layers.

The above-described methods provide a heat pump with dehumidifying and desalination properties in which the dehumidified and desalinated air, even with total recooling to the outside air level, for example through the tower walls or through mechanical means for free indirect cooling, such as a plate heat exchanger operated with fresh air Dew point can not be reached again and can maintain and guarantee a maximum relative humidity of less than 60% relative humidity through targeted dehumidification, so that a linear increase in corrosion is excluded and the risk of corrosion is permanently significantly reduced.

A first device for air treatment in wind power plants, especially in offshore wind energy plants, with a tower at the top of a gondola with a generator and at least one rotor blade and in the interior heat-dissipating electrical and electronic units such as switchgear, switching devices, transformers , Frequency converter and the like are arranged in an aggregate module of the tower and having at least one air inlet opening and an air outlet opening, is sucked through the air inlet opening from the environment of the tower moist and salty outside air, characterized by an air treatment device with a heater or an air heater for heating the outside air or in an air treatment or desalination unit desalinated and dehumidified outside air and a high-performance filter for filtering the particle-salted salt aerosols in the outside air or desalted and dehumidified outside air and the supply of heated supply air through the aggregate module in the tower and in the nacelle. This simple air treatment device makes it possible to deposit the particle-crystallized salt aerosols in a high-performance filter as salt particles by heating the outside air to a relative humidity of 40%. The associated significant reduction of the residual salt content and thus the risk of corrosion in the unit module and in the interior of the tower and in the nacelle, however, can not ensure under all climatic conditions and throughout the year that the air flow in the aggregate module and in the interior of the tower and the nacelle in the Is maintained, so that on the one hand the heat dissipated by the electric and electronic units is dissipated sufficiently safe and on the other hand, a risk of corrosion inside the tower and the nacelle can be excluded. Nor is emergency operation possible in the event of storm, light wind, accidents and maintenance.

An improved device for air treatment in wind power plants, especially in offshore wind energy plants, with a tower at the top of a gondola with a generator and at least one rotor blade and in the interior heat-dissipating electrical and electronic units such as switchgear, switching devices, transformers , Frequency converter and the like are arranged in an aggregate module of the tower and having at least one air inlet opening and an air outlet opening, is sucked through the air inlet opening from the environment of the tower moist and salty outside air, is characterized by an air treatment device with one of an evaporator for Reduction of the absolute moisture content of the supplied outside air or the outside air desalinated and dehumidified in an upstream air treatment or desalination unit, a condenser or a reheat coil for reheating the outside air a uf a relative humidity of 40% or less and a compressor dehumidifying heat pump, and with a high performance filter for salt separation.

With the improved air treatment device is achieved by cooling the humid and salty outside air while reducing the absolute moisture content of the outside air and the subsequent reheating a moisture level of the treated outside air of less than or equal to 40% relative humidity, so that the salzaerosols still contained in the outside air crystallized and can be deposited in a high performance filter. After the dehumidification and desalination of the outside air, the supply air flows freely and without special air supply systems into or through the aggregate module and through the upper part of the tower to the nacelle. This will achieve that the dehumidified and desalinated supply air even at total recooling to the temperature value of the outside air due to cooling on the way from the unit module to the nacelle at any point the low level of dew point, ie a relative humidity of 100%, can reach what the risk of condensation in the entire wind energy plant and thus the risk of corrosion significantly reduced. However, this does not allow for an optimal energy solution and targeted airflow in the aggregate module or inside the tower.

An optimized air treatment system with a third, optimal device for air treatment in wind power plants, in particular in offshore wind power plants, with a tower, at the upper end of a nacelle with a generator and at least one rotor blade and in the interior heat-releasing electrical and electronic units such as switchgear, switching devices, transformers, frequency converters and the like are arranged in an aggregate module of the tower and having at least one air inlet opening and an air outlet opening, wherein via the air inlet opening from the environment of the tower moist and salty outside air is sucked in, is characterized by an air treatment device with an air treatment device with recuperative heat recovery system and hermetically separated first and second flow paths, wherein the first flow path sucked through the air inlet opening outside air to d it leads to the interior of the tower with the exception of the aggregate module delivered supply air and the second flow path in recirculation mode supply air to the unit module and sucks exhaust air or return air from the unit module.

Preferably, the air treatment device with recuperative heat recovery system includes a plate heat exchanger, which is arranged in the flow direction of the first flow path to a connected to the air inlet opening air treatment device for desalination of the sucked outside air.

The optimized air treatment system ensures a powerful cooling of the surface heat dissipation of the electric and electronic units, a controlled temperature maintenance in the tower to the nacelle by controlled heat transfer with power from the waste heat of the electric and electronic units and hermetically separate two air streams that always outside air contaminated with salt no longer flows freely through the aggregate module and thus can not contaminate the electrical and electronic units. Preferably, the plate heat exchanger on the inlet side of the cooled down in the evaporator of the dehumidification heat pump outside air adjustable bypass flaps, with which the number of plates of the plate heat exchanger can be set, which are used in the outside air supply air flow for energy exchange or to be passed to the energy exchange, so that on the adjustment the bypass valves influence the energy exchange and thus the temperature and / or humidity behavior of the air treatment device can be taken and the bypass valves can be included in a temperature and humidity control of the optimized air treatment system.

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

In principle, the outside air fan can be arranged both on the suction side and on the pressure side. The latter, for example, when the outside air fan is already part of an existing, conventional air handling unit and the air treatment device is retrofitted. However, there are advantages to the arrangement of the outside air fan on the suction side of the air treatment unit, as it is located in dry, salt-free air, which considerably reduces the risk of corrosion of the outside air fan and therefore requires only a low level of material quality from the outside air fan. In addition, the arrangement of the outside air fan on the suction side allows placement of the Außenluftventila- sector, which are possible and suitable from the unit module on all intermediate decks of the tower to the nacelle as a site.

By arranging a supply air duct from the air treatment device to the interior of the tower separate from the unit module, the desalted and dehumidified supply air in the supply air duct is guided in a consistent continuation of the separation of the two flow paths through the plate heat exchanger, from the circulating air circulating in the unit module to the inside of the tower Moisture or salt aerosols still contained in the supply air can not reach the sensitive electrical and electronic devices in the aggregate module. To ensure that, on the one hand, the supply air is treated in such a way that the dehumidified and desalinated supply air delivered to the interior of the tower and / or the aggregate module does not reach the dew point again, even if it cools down to the value of the outside air, and a maximum relative humidity value through targeted dehumidification performance On the other hand, the electric and electronic units arranged in the tower and the nacelle of the wind power plant are sufficiently cooled for safe, permanent operation, the output of the air treatment device is with a first flow path of a recuperative heat recovery system and air handling unit hermetically separated from each other first and second flow paths, wherein the first flow path emitted at the output of the air treatment device supply air as cooled supply air to the interior of the tower and / or the Gives subassembly module and in the second flow path outside air (AL) is sucked by means of an additional fan and delivered to an exhaust air connection.

Since it may happen in certain regions, that although the air is sufficiently desalinated and dehumidified, but that the output into the tower and / or in the nacelle of the wind energy supply air has a temperature level that is too high for cooling the units or If cooling is not completely sufficient, a mechanical cooling device is additionally arranged in the flow path of the supply air to the cooled supply air.

Preferably, the supply air duct is connected to a heat exchanger which emits heat energy taken up by the electrical and electronic units arranged in the unit module to the supply air flow of the first flow path leading into the interior of the tower, wherein the heat energy delivered by the heat exchanger to the supply air flow depends on the heat energy Temperature in the interior of the tower and / or the nacelle adjustable and at least one temperature in the interior of the tower and / or the nacelle detecting temperature sensor is connected to a control device.

In an analogous manner, the circulating air is conducted in the supply air and exhaust air ducts from the plate heat exchanger to and from the unit module, so that the circulating air flow is selectively guided via the air ducts in the individual floors of the unit module, the heat dissipated by the heat-emitting electrical and electronic units dissipated and thus prevents residual moisture and residual salt content in the Aggregate module can penetrate, the air ducts also cause a targeted air flow and cooling, so that the heat-emitting electrical and electronic units are effectively cooled regardless of their location.

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

In order to lower 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, the further high-performance filter is arranged in a bypass with two shutter flaps whose position determines the proportion of the circulating air flow as a function of a humidity measurement. which is passed through the arranged in the bypass channel high-performance filter.

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

Both in the outside air supply air flow and in the recirculation air, each consisting of an evaporator or cooler, condenser or reheat register and compressor dehumidification heat pump can be arranged, the recirculation dehumidifying heat pump preferably arranged in the exhaust duct of the circulating air in the flow direction in front of the high-performance filter is used to eliminate salt particles and aerosols in the circulating air stream, which may leak into the unit module, possibly through leaks, while mounting or the like.

By bypassing the overpressure in the circulating air flow path, which branches off from the supply air duct and is connected to the circulating air flow path at the connection of the circulating air Entfeuchtungswärmepumpe with the high-performance filter, it is achieved that the circulating air flowing through the unit module not by currents from other areas of the Wind turbine is contaminated with salty air, the required amount of bypass air is very small, does not significantly affect the moisture content of the circulating air and prevents negative flows from the range of Tower of the wind turbine or the air inlet opening penetrate into the unit module, so that the required amount of air is only slightly.

Furthermore, an independent heating device, preferably an electric heating coil, can be arranged in the supply air flow path of the air treatment device behind the plate heat exchanger and upstream of the high-performance filter.

By a bypass in the flow path of the circulating air flow with controllable Bypassklap- pen and a bypass line for passing the circulating air flow to the high-performance filter and a bypass in the outside air supply air flow path with independently controllable bypass valves and a bypass line for passing the supply air flow to the high-performance filter can be set with a control device such a position that the air flows at favorable humidity values either through the high-performance filter or be guided over the bypass lines to the high-performance filters.

This ensures that salt crystals, which accumulate in the high-performance filters and are stored on the "dirty" side, do not decompose again to aerosols at elevated humidity values and penetrate to the "pure" side of the high-performance filters and through the increased humidity in the aggregate module or into the tower or the nacelle are carried.

The provided in the flow path of the circulating air flow dehumidification heat pump, which is arranged in front of the heat from the waste heat of the electrical and electronic units in the aggregate module heating device and consists of an evaporator / cooler, compressor, and a first capacitor, can arranged around a in Außenluft- supply air second capacitor can be extended, which is associated with the first capacitor and with this common or mutually operable. In this arrangement of an air treatment system, the dehumidifying heat pump disposed in the outside air supply air flow path consists of an evaporator / condenser, a compressor, a first condenser, and a second condenser with a reciprocal operation.

The dehumidification heat pump systems designed in this way in the circulating air and fresh air supply air flow cause an emergency heating, for example for frost-free maintenance of the air treatment device, or for additional desalination and dehumidification at low temperatures Temperatures and downtimes of the wind energy plant, since the Entfeuchtungswärmepumpensysteme in outdoor air supply air and circulating air flow through a very high efficiency with lowest power consumption provide high heating power, whereas an electric heater with the same thermal output would cause more than five times the power consumption. As a result of the arrangement of the second condenser of the circulating-air dehumidification heat pump in the outside air supply air flow, the energy output can be switched over or regulated from 0 to 100%, depending on the requirement and the heat requirement. Since the dehumidification heat pump system also has two condensers in the outdoor air supply air flow, the heat energy can be discharged in the air direction before or after the plate heat exchanger as required, and regulated from 0 to 100%.

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 targeted in the upper region of the tower and closer can be brought to the nacelle, the air jet at high speed on its flow path inducing permanent air from all sides of the tower, so that air stratification and temperature stratification torn and secondary flows are avoided.

The most centric arrangement of the jet nozzle avoids a distraction and leaning of the flow to the tower wall and thus the so-called Koander effect. For the introduction of air, a nozzle or diffuser shape is chosen because it keeps the static pressure losses low.

On mechanical decks of the tower arranged mechanical air conveyors, in particular fans, cause an increase in the dynamic velocity of the supply air flow, because the introduced via the outside air fan air quantity penetrates openings in decks or elevator bushings due to the large pressure behavior, which can develop an uncontrolled flow behavior in the tower and the nacelle ,

In addition, the mechanical air conveyors can preferably with the waste heat of the unit module arranged in the heat-dissipating electrical and electronic units fed heating devices are connected, which is advantageous due to the Abkühleffektes by the tower walls in conjunction with the long flow paths. The temperatures in the entire tower can be made more uniform compared to a single central heating and influence the temperature condensation behavior in the tower advantageous.

In order to ensure that in subareas of the wind power plant in which larger heat loads occur, sufficient cooling of aggregates takes place without the dehumidified and desalinated supply air delivered to the interior of the tower and / or to the module module even when it cools down again The value of the outside air reaches the dew point again and maintains a maximum relative humidity of less than 60% relative humidity by means of targeted dehumidification. In parts or areas of the tower or the nacelle of the wind energy installation, an air treatment unit with recuperative heat recovery system and hermetically separated first and second flow paths are arranged, wherein the first flow path leads outside air to the exhaust air and the second flow path in the recirculation mode sucks incoming air and discharges as indirectly freely cooled supply air.

In addition, with increased cooling demand in the flow path of the indirectly freely cooled supply air, a mechanical refrigeration device can be arranged.

To use the cooling effect of the powerful steel tower of the wind energy plant at least one speed increasing device, preferably a fan and a nozzle, arranged in the tower, the air at high speed obliquely upwards, on the tower wall along upwards and in the tower a rotary motion or vortex flow generated, wherein the nozzle preferably has a round shape or a flat-jet shape.

By this arrangement, a speed increase by nozzle effect is selectively produced, in conjunction with the Koanda effect produces an eddy current in the entire tower and increases the heat transfer coefficient.

The method according to the invention and the arrangement according to the invention can also be used in wind power plants which are exposed to other stresses, for example in desert or steppe regions with heavy sand loading of the intake outside air, which necessitates the use of special filters in the air treatment device or in the aftertreatment device. On the basis of several embodiments shown in the drawings, the essential features and advantageous embodiments of the invention and the advantages achieved thereby are explained in more detail. Show it:

Figure 1 is a trained according to the prior art conventional device for the air treatment and air flow of an offshore wind energy plant.

Fig. 2 is a schematic representation of the aggregates of a conventional

Air treatment or desalination apparatus for desalination of the sea air and for generating an overpressure in the interior of the tower of an offshore wind power plant;

Fig. 3 is a Mollier-h, x-diagram for humid air for explaining the receptivity of water in the air at different air temperatures;

Fig. 4 is a graph showing the corrosion rate of metals as a function of moisture film thickness;

5 shows a representation of the corrosion rate of iron as a function of the relative humidity;

6 shows a h, x diagram for humid air for illustrating the region of the "critical humidity" in connection with a fictitious weather bubble;

7 is a schematic representation of a simple air treatment system for aftertreatment and supplementary air treatment in an offshore wind power plant;

Fig. 8 is a schematic representation of a portion of a tower of an offshore

Wind energy plant with a simple air treatment device 3 for reducing the salt content, dissipating the heat emitted by the electric and electronic units and improving the moisture retention; Fig. 9 is a schematic representation of a portion of a tower of an offshore

Wind energy plant with an improved air treatment system for

Reduction of the salt content, removal of the heat emitted by the electrical and electronic aggregates and improvement of the moisture retention;

FIG. 10 is a schematic representation of an improved air handling unit having a dehumidification heat pump and a high efficiency filter of the improved air handling system of FIG. 9; FIG.

Fig. 11 is a Mollier-h, x-diagram for humid air for explaining the improved air treatment system of Fig. 9;

FIGS. 12 and 13 show two embodiments of a combination of an improved air treatment device according to FIG. 10 with a conventional air treatment or desalination device;

14 is a schematic representation of an optimized air treatment system for aftertreatment and supplementary air treatment with an optimal air treatment device in an offshore wind

Power plant;

FIG. 15 shows an air guidance and system diagram of a first embodiment of an optimal air treatment device for the optimized air treatment system according to FIG. 14; FIG.

16 shows a longitudinal section through the housing of the first embodiment of the optimal air treatment device according to FIG. 15;

17 shows an air guidance and system diagram of a second embodiment of an optimal air treatment device for the optimized air treatment system according to FIG. 14;

FIG. 18 shows an air guidance and system diagram of a third embodiment of an optimal air treatment device for the optimized air treatment system according to FIG. 14; FIG. 19 shows a longitudinal section through the housing of the third embodiment of the optimal air treatment device according to FIG. 18;

20 to 22 Luftführungs- and system schemes of other embodiments of an optimal air treatment device for the optimized air treatment system of FIG. 14;

FIG. 23 shows a Mollier-h, x diagram for outside air and return air (circulating air) in summer and winter operation of an optimum air treatment device according to FIG. 22; FIG.

FIGS. 24 to 28 air guiding and system diagrams of further embodiments of an optimal air treatment device for the optimized air treatment system according to FIG. 14;

FIGS. 29 to 31 show three embodiments of a combination of the optimal air treatment device according to FIG. 28 with the units of a conventional air conditioning or desalination apparatus;

32 shows an offshore wind power plant with an optimized air treatment system and a reheating coil or heat exchanger and a jet nozzle for blowing a supply air flow into the tower of the offshore wind power plant at high speed;

Fig. 33 is a Mollier-h, x diagram for explaining the effect of the optimized one

Air treatment system with the optimal air treatment device;

FIG. 34 shows an offshore wind power plant with several intermediate decks and speed-increasing devices designed as a nozzle or diffuser; FIG.

FIG. 35 shows a detailed representation of an intermediate deck with bypass flows and a nozzle with a mechanical air delivery device; FIG. Fig. 36 is a schematic representation of an air treatment system for a

Offshore wind energy plant in conjunction with a conventional air treatment or desalination plant;

FIG. 37 shows an offshore wind power plant with mechanical air conveyors and heaters in several intermediate decks; FIG.

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

FIG. 39 shows a schematic representation of an optimized air treatment system with a combination of a conventional air treatment and / or desalination device, an improved air treatment device and a plate heat exchanger for free, indirect cooling of the supply air flow delivered into the tower of a wind energy installation;

Fig. 40 is a schematic representation as in Figure 39 with an additional mechanical cooling of the supply air flow in the tower of the wind energy plant.

41 shows a schematic representation of an optimized air treatment system for partial areas of a wind power plant for additional or independent cooling of units;

FIG. 42 shows a schematic representation as in FIG. 41 with an additional mechanical cooling; FIG.

Fig. 43 is a schematic representation of an air treatment system for a

Wind power plant with supplementary cooling or Entwärmungseinrich- lines according to FIGS. 39 to 42;

Fig. 44 is a schematic representation of FIG. 43 with registered therein

Temperature examples for the area of the German North Sea and Fig. 45 is a schematic representation of the increase of the cooling effect by the

Tower walls of the tower of a wind energy plant.

So far, in connection with the conventional air treatment or desalination apparatus 2 shown schematically in FIG. 2, the outside air AL sucked from the environment of an offshore wind energy installation 1 according to FIG. 1 is roughly desalinated and dehumidified and continues to flow in an uncontrolled, turbulent and free air flow moist and salzaerosols containing supply air ZL on the arranged in the aggregate module 15 of the tower 10 electrical and electronic units 16 in the upper part of the tower 10 to the nacelle 1 1. There flows the tower 10 and the nacelle 11 supplied supply air ZL by the outside air fan 25 in the air treatment or desalination unit 2 shown in FIG. 2 generated overpressure as exhaust air FL. The residual salt content of the Zuluft ZL flowing through the aggregate module 15 and the tower and the nacelle is thereby a hundred times greater than the desired value, so that the electrical and electronic units 16 and in the tower 10 and the nacelle 11 arranged devices and inner walls of the tower 10 are exposed to strong corrosion due to the influence of the salt and the residual moisture of the supply air ZL.

In order to significantly reduce the residual salt content, according to the schematic illustration of an offshore wind energy installation 1 according to FIG. 3, the moist and saline outside air AL drawn in via the air inlet opening 14 from the environment of the tower 10 is roughly desalinated in the air treatment or desalination apparatus 2 according to FIG and dehumidifies. The roughly desalinated and dehumidified outside air AL is delivered to a simple air treatment device 3 in which the outside air AL is heated and the salt aerosols crystallized thereby into particles in the outside air AL are filtered out. The supply air ZL discharged by the air treatment device 3 flows through the aggregate module 15 in free, uncontrolled flow, absorbs the radiant heat emitted by the electrical and electronic units 16 in the aggregate module 15 and exits the aggregate module 15 as heated supply air ZL 'in an uncontrolled, spinning air flow in the upper part of the tower 10 and in the gondola 11 a. There, the supply air ZL 'flows through the overpressure generated by the outside air fan 25 in the air treatment or desalination unit 2 according to FIG. 2 as exhaust air FL into the environment of the offshore wind power plant 1. 4 shows, in an enlarged detail, the region of the aggregate module 15 with the conventional air treatment device 2 arranged below the aggregate module 15 and the simple air treatment device 3, which contains a heating device or an air heater 31 and a high-performance filter 32 and those of the air conditioning or desalination device 2 processed outside air AL as supply air ZL outputs to the unit module 15. In the aggregate module 15, the supply air ZL flows past the electrical and electronic units 16, absorbs the heat energy emitted by the electrical and electronic units 16 and enters the upper part of the tower 10 above the unit module 15 as heated supply air ZL ' whereupon the heated supply air ZL 'ascends as an uncontrolled, turbulent flow to the nacelle 11.

The simple air treatment device 3 is based on the finding that salt aerosols crystallize to particles at a relative humidity of the outside air of less than 40%. If the outside air AL is now heated to such an extent that the relative humidity characteristic of 40% in the Mollier-h, x-diagram is reached, then the salt aerosols crystallized into particles can be deposited as salt particles in the high-performance filter 32 arranged downstream of the heating device 31.

Preferably, the heating device 31 is supplied with energy from the waste heat of the electrical and electronic units 16 in the unit module 15, for example by liquid cooling of at least part of the electrical and electronic units 16 and re-cooling of the heat absorbed in the cooling liquid in a heater 31 designed as an evaporator.

Although the above-described simple air treatment device 3 ensures a significant reduction of the residual salt content and thus significantly reduces the risk of corrosion in the unit module 15 and inside the tower 10 and in the nacelle 1 1, but can not ensure under all climatic conditions and year-round that the air flow in the Aggregate module 15 and inside the tower 10 and the nacelle 1 1 is maintained in such a way that on the one hand, the heat emitted by the electrical and electronic units 16 heat is dissipated sufficiently safe and on the other hand, the risk of corrosion inside the tower 10 and the nacelle. 1 1 can be excluded.

Thus, in the winter months, although the 40% -moisture of the Mollier-h, x-diagram is reached quickly and there is a sufficient temperature range, the of the heat dissipates the electric and electronic units 16 of the aggregate module 15 without the risk of overheating in the unit module 15, the heated supply air ZL 'entering the upper part of the tower 10, however, starts to spin due to the low flow velocity in the large tower cross section There uncontrolled flow movements, which lead to secondary currents that fall in certain areas on the inner wall of the tower 10 to the dew point and lead to condensation of Zuluftstromes 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 bound in salt aerosols in the supply air ZL will lead to corrosion on the electrical and electronic units 16 in the aggregate module 15 and the waste heat the electrical and electronic units 16 additionally heated supply air ZL 'on the inner wall of the tower 10 and the nacelle 1 1 leads.

In the summer months emitted from the simple air treatment device 3 to the unit module 15 supply air flow ZL also absorb the additional energy from the radiation of the electrical and electronic units 16 in the unit module 15, which at a correspondingly high temperature of the outside air AL and after the additional heating by the Air heater 31 for crystallizing the salzaerosols and separating the salt particles thus formed in the high-performance filter 32 can lead to a critical increase in temperature in the aggregate module 15, if not allowed a high threshold temperature in the aggregate module 15 and / or a possible overheating in the aggregate 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. In order to ensure the greatest possible safety in terms of overpressure, salt-free, temperature maintenance, humidity and avoid condensation of the delivered to the unit module 15 and the tower 10 and the nacelle 1 1 supply air ZL or heated ZL 'during this year, an emergency operation is required that can be ensured only insufficiently with the simple air treatment device 3 by, for example, the air heater 31 of the simple air treatment device 3 is connected to an electric afterheating device, which is fed in emergency operation from the supply network to which the wind energy system emits electrical energy in normal operation. Furthermore, a temperature and humidity retention in the unit module 15 and inside the tower 10 and the nacelle 1 1 without thermodynamic treatment of the outside air AL or supply air ZL is not possible, especially since the available heat from the heat radiation of the electrical and electronic units 16 and the energy from the electric and electronic units 16 to a cooling liquid for heat dissipation and powering the air heater 31 and an evaporator of the simple air treatment device 3 between full load and partial load fluctuations and in emergency mode, ie at standstill of the wind energy plant, not available at all are.

FIGS. 5 to 6 show an improved air treatment device 4, which is described in more detail below and explained in its function.

According to FIG. 6, the improved air treatment device 4 contains an evaporator 41, to which the desalinated and dehumidified outside air AL discharged from the conventional air treatment device 2 is sucked in via the air inlet opening 14 from the environment of the tower 10 as moist and saline outside air AL Air treatment or desalination unit 2 as shown in FIG. 2 was partially desalinated and dehumidified. Furthermore, the improved air treatment device 4 includes a condenser or reheat coil 43 and a compressor 42, which together with the evaporator 41 form a dehumidifying heat pump, and a high-efficiency filter 44 for salt separation. The partially desalinated and dehumidified outside airflow AL discharged from the conventional treatment apparatus 2 is discharged from the outside air fan 25 arranged in the flow path of the outside air AL in the air conditioning or desalination apparatus 2 shown in FIG. 2 to the improved air handling unit 4 in which the outside air AL is supplied by means of the evaporator 41 is cooled to a lower level, wherein the absolute humidity of the outside air AL is lowered.

The cooling of the moist and saline outside air AL while reducing the absolute moisture content of the outside air AL, which takes place through the arrangement of a deicing system in the evaporator 41 even 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. Through this process, the salt aerosols still contained in the outside air AL are crystallized and can be deposited by downstream in the flow direction of the outside air AL Hochleistungsfilter 44. After dehumidification and desalination of the outside air AL supply air ZL flows from the high-performance filter 44 of FIG. 5 freely and without special air flow systems in or through the unit module 15 and through the upper part of the tower 10 to the nacelle 1 1 and can there by leaks due to by means of the outside air fan 25 of the air treatment or desalination 2 generated excess pressure escape as exhaust air FL.

This process also ensures that the dehumidified and desalinated supply air ZL even at total recooling to the temperature value of the outside air AL due to cooling on the way from the unit module 15 to the nacelle 11 through the non-insulated steel walls of the tower 10 at any point in the interior of the tower 10 the low level of the dew point, d. H. a relative humidity of 100%, can reach. For example, the value of the relative humidity in the entire interior of the tower 10 is about 70% relative humidity, so that the risk of condensation in the entire wind energy plant and thus the risk of corrosion by reducing the moisture is significantly reduced.

The operation of the improved air treatment device 4 according to FIGS. 5 and 6 with four temperature examples, in which a relative humidity of the outside air AL of 100% is assumed, will be explained with reference to the Mollier-h, x diagram shown in FIG.

In the first example, the temperature T11 of the outside air AL = 20 ⁰ C and is cooled in the evaporator 41 to a temperature T12 = 14 ⁰ C. The absolute humidity of the outside air AL is reduced to about 10 g / kg. By subsequent heating of the cooled and dehumidified outside air AL in the condenser or reheat coil 43 to a temperature T13 of about 32 ⁰ C, the relative humidity of the outside air is reduced to about 35%, so that the Salzaerosole contained in the outside air AL in We - Essentially crystallized and the crystallized salt aerosols and contained in the outside air AL salt particles in the high-performance filter 44 can be deposited.

The outside air AL dehumidified and desalinated in the air treatment device 4 is discharged into the interior of the tower 10 as supply air ZL to the unit module 15 and after passing through the unit module 15 and receiving the thermal energy emitted by the electric and electronic units 16 as heated supply air ZL '. give, by the inclusion of additional heat energy, a further increase in temperature compared to the temperature T13, which is associated with a further decrease in the relative humidity. A re-cooling of the heated supply air ZL 'on the way through the interior of the tower 10 and the nacelle 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 up to the value of the outside temperature T1 1st from 20 ^° C., that is to say to point T14, so that the air in the interior of the tower 10 and the nacelle 11 can not fall back to the dew point line, ie to the line of 100% relative humidity, but according to the Mollier h, x-diagram of FIG. 7 at a value of relative humidity of only about 70% remains. It still remains unconsidered that the absorption of heat energy in the aggregate module 15 causes an increase in the temperature T13, so that the relative air humidity is still above this value of 70%.

In the second example, a temperature T21 of the outside air AL of 14 ⁰ C is assumed. The moist and saline outside air AL is cooled along the dew point line in the evaporator 41 to a temperature T22 of about 9 ⁰ C and thereby lowered to an absolute humidity of about 7 g / kg. By subsequent heating in the condenser or reheat coil 43 of the dehumidification heat pump to a temperature T23 of about 25 ⁰ C, the relative humidity of the outside air is reduced to about 38% and the salt salts thus crystallized and contained in the outside air AL salt particles are in the high-performance filter 44th deposited.

In the third example, a temperature T31 of the outside air AL of 7 ^° C. is assumed. The moist and salty outside air AL is cooled down along the dew point line in the evaporator 41 to a temperature T32 of approximately 2 ^° C. and thereby to an absolute humidity of lowered about 4 g / kg. By subsequent heating in the condenser or reheat coil 43 of the dehumidification heat pump to a temperature T33 of about 14 ⁰ C, the relative humidity of the outside air is reduced to about 40% and the salt crystals so salted and salt particles contained in the outside air AL are in High-efficiency filter 44 deposited.

In the fourth example, it is assumed that a temperature T41 of the outside air AL of -5 ⁰ C. The moist and salty outside air AL is steam cooled along the dew point line 41 in comparison to a temperature T42 of about -12.5 ⁰ C and thereby lowered to an absolute moisture content of about 1 g / kg. By subsequent heating in the condenser sator or reheat coil 43 of the dehumidification heat pump to a temperature T43 of about 1 ⁰ C, the relative humidity of the outside air is reduced to about 25% and the thus crystallized salt aerosols and salt particles contained in the outside air AL can be deposited in the high-performance filter 44.

In the second to fourth example, the fresh air AL dehumidified and desalinated in the improved air treatment device 4 is also supplied as supply air ZL to the unit module 15 and after passing through the unit module 15 and receiving the heat energy radiated by the electric and electronic units 16 as the heated supply air ZL 'discharged into the interior of the tower 10. Here, the dehumidified and desalinated in the air treatment device 4 outside air AL as supply air ZL to the unit module 15 and after flowing through the unit module 15 and receiving the radiated from the electrical and electronic units 16 thermal energy as heated supply air ZL 'in the interior of the tower 10 is delivered , wherein the absorption of additional heat energy, a further temperature increase compared to the temperatures T23, T33 and T43 takes place, which is associated with a further decrease in the relative humidity.

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

The four examples illustrated in FIG. 7 on the basis of a Mollier h, x diagram make it clear that the dehumidifying process is completely achieved solely by the dehumidification heat pump formed by the evaporator 41, the condenser or reheat coil 43 and the compressor 42. The heat radiation of the unit module 15 arranged in the electrical and electronic units 16 and / or a possible reheating of the waste heat of these units is an additional positive effect, the However, in standstill of the wind power plant in weak or strong winds, in case of failure or shutdown for maintenance purposes is not available. 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.

FIGS. 8 and 9 show two variants of a combination of an improved air treatment device 4 with a conventional air treatment device 2 and will be explained in more detail below.

In the first variant according to FIG. 8, the moist and saline outside air AL sucked in via the air inlet opening 14 from the environment of the tower 10 by means of the outside air fan 25 is not conducted via the conventional air treatment device 2 according to FIG. 2, but only via a first droplet separator 21 first simplified air treatment device 2 'and then supplied as dehumidified outside air AL to the evaporator 41 for cooling and dehumidifying. After heating in the condenser or reheat coil 43, the crystallized salt aerosols and salt particles contained in the outside air AL are deposited in the high-performance filter 44, wherein the air flow through the in this embodiment, preferably on the suction side of the reduced air treatment device 2 'and reduced to the mist eliminator 21 the improved air treatment device 4 is arranged and the dehumidified and desalinated supply air ZL and desalted in the high-performance filter 44 outside air AL as supply air ZL in free air flow to the unit module 15 and as heated supply air ZL 'in the interior of the tower 10 and the nacelle 11 is discharged.

In the arrangement according to FIG. 8, therefore, the coalescence separators 22 and 23 according to FIG. 2 are omitted because the dehumidification heat pump formed by the evaporator or condenser 41, condenser or reheat register 43 and compressor 42 results in dehumidification and heating of the dehumidifying heat pump Outside air AL is carried out in such a way that first water and thus also salt sols are deposited and crystallize the remaining salt components after heating by means of the dehumidification heat pump, when a value of relative humidity of less than or equal to about 40% is reached. Subsequently, the high-performance filter 44 ensures the deposition of the crystallized salt. 9 shows the arrangement of both the two mist eliminators 21, 24 and a coalescence separator 22 in an air treatment unit 2. In this embodiment, the outside air AL sucked from the environment by means of the outside air fan 25 is discharged via a first droplet separator 21, a coalescence - Separator 22 and a second droplet 24 of the air treatment unit 2 "passed there partially dehumidified and desalted and then supplied as partially dehumidified and desalinated outside air AL shown in Fig. 8 dehumidification heat pump, where the outside air AL is cooled and dehumidified in the evaporator 41, in the condenser or reheat coil 43 is heated and the salt salts thus crystallized and salt particles contained in the outside air AL are deposited in the high-performance filter 44, before the dehumidified and desalinated supply air ZL in free air flow to the unit module 15 and as heated supply air ZL 'in the interior of the tower 10 and the nacelle 11 is discharged.

The outside air fan 25 arranged in FIGS. 8 and 9 on the suction side of the air treatment device 2 'or 2 "and the improved air treatment device 4 can alternatively also be on the pressure side, ie before the first droplet separator 21 of the air treatment device 2' or before the first droplet separator 21 of the improved air treatment apparatus 2 "or between the air treatment apparatus 2 'and 2" and the improved air treatment apparatus 4. However, the arrangement of the outside air fan 25 on the suction side of the air treatment apparatus 2' and 2 "and the improved air treatment apparatus 4 has the substantial advantage that the outside air fan 25 is arranged not in humid air, but in relatively dry air, which is also free of salt, which has advantages with respect to the corrosion behavior of the outside air fan 25.

In Fig. 10, an optimized air treatment system 6 with an optimal air treatment device 5 and air ducts 75, 76 shown in the unit module 15, with which under any climatic conditions, in the year-round operation and in emergency mode with stationary wind energy system optionally sucked on the air treatment unit 2 humid and salty outdoor air AL is dehumidified, filtered and desalted, a cooling of arranged in the unit module 15 heat-dissipating electrical and electronic units 16 is performed, a positive pressure in the entire wind energy system ensures and a risk of corrosion is essentially excluded. According to the schematic representation according to FIG. 10, the sucked in moist and saline outside air AL in the air treatment unit 2 is only partly or coarsely desalted and partially dehumidified, the still moist and salty outside air AL 'an optimal air treatment device 5 and supplied from this as dehumidified and desalinated supply air ZL guided through an inlet air duct 74 through the unit module 15, without coming into contact with the air in the unit module 15, and discharged above the unit module 15 to the overlying free space 100 of the upper part of the tower 10.

At the end of the supply air duct 74 optionally a Nachheizregister or heat exchanger 8 can be arranged with control valve, with which the temperature in the upper region of the tower 10 and in the nacelle 1 1 is controlled. The heat exchanger 8 is fed from the waste heat of the heat generating electrical and electronic units 16 in the unit module 15. The heat exchanger 8 can alternatively or optionally also be arranged directly in or on the optimized air treatment device 5 or at any other point in the supply air channel 74. In addition, it is possible to set up the postheater or the heat exchanger 8 as a statically acting element freely in the tower 10, if you can do without the influence on the flow behavior.

The effect and positive consequences of the heat exchanger 8 are that in order to avoid condensation within the tower 10 and the nacelle 1 1, the air is heated so far through the heat exchanger 8, i. a temperature increase is effected, that even by the cooling effect of the tower walls and a drop in temperature in the tower 10 and the nacelle 1 1, the dew point is not reached. Preferably, a sensor for the temperature measurement and control in the nacelle 1 1 is arranged in front of the air outlet due to the generated overpressure.

However, this effect is only achieved in conjunction with an evaporator of a dehumidification heat pump arranged in the outside air flow AL, which initially causes marked dehumidification (precipitation by condensation) with only slight cooling, so that the air, which completely recirculates when flowing through the tower 10 by the cooling of the tower walls to the temperature value of the outside air does not fall back to the humidity characteristic 100%, but can fall at the same low temperature only to 80% relative humidity. As a result of the hermetically separated guidance of two air streams in the optimized air treatment device 5, of which the first flow path according to FIG. 11 is guided from the air inlet opening 14 via an air treatment device with recuperative heat recovery system 51, preferably a plate heat exchanger, alternatively also a heat pipe or a dehumidification heat pump. during the heat exchanging connection with the first flow path, the second flow path leads in a closed circuit through the aggregate module 15 and delivers the heat energy absorbed by the heat emission of the electric and electronic units 16 via the air treatment device with recuperative heat recovery system 51 to the first flow path, from which, excluding the aggregate module 15 heated, dehumidified and desalted air with pressure to the interior 100 of the tower 10 and the nacelle 1 1 is discharged. This ensures that the still contaminated with salt outside air AL 'no longer flows freely through the unit module 15 and thus the electrical and electronic units 16 can no longer contaminate.

The air treatment device 5 not only causes dehumidification and desalination of the discharged from the air treatment unit 2 outside air AL ', but also takes over the cooling of the unit module 15 by a targeted air extraction from the individual floors or platforms of the unit module 15 via recirculation air ducts 76 and a targeted air supply via Recirculation air supply ducts 75 in the individual floors or platforms of the unit module 15. If the supply air ZL (UL) the circulating air UL is not supplied to the individual floors of the unit module 15, but injected, for example, in the lower floor and deducted in the upper floor, so is a appropriate air duct between the floors of the unit module 15 is provided.

In this recirculation process, the energy is exchanged via the arranged in the optimized air treatment device 5 plate heat exchanger 51 between the outside air flow 1 and the guided in the air ducts 75, 76 circulating air flow UL. The outside air flow AL 'or supply air flow ZL thus indirectly cools the recirculating air flow UL. In this case, the circulating air flow UL, the heat, which results from the surface heat output of the electrical and electronic units 16, to the supply air flow ZL, so that the heated supply air flow ZL "shown in FIG. 10 preheated in the upper tower 10 and thus in the nacelle 1 1. At extremely low temperatures, additional reheating can take place through the optionally arranged heat exchanger 8. But even without the arrangement of air ducts 75, 76 for targeted guidance and delivery of the circulating air flow UL to the arranged in individual levels or floors of the unit module 15 electrical and electronic units 16 results in a significant improvement, because the circulating air flow UL, by the Plate heat exchanger 51 is hermetically separated from the guided in the supply air duct 74 supply air flow ZL, contains no salt particles or aerosols, is also cooled and dissipates the surface heat of the electrical and electronic units 16. 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 ef- fektivere solution

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

Alternatively, the unit module 15 can also be arranged below the air inlet opening 14 for the outside air AL, so that the optimized air treatment device 5 delivers the heated and desalinated air directly to the upper, free part of the tower 10, while the circulating air flow UL into the below the optimized air treatment device 5 arranged unit module 15 is discharged, where the circulating air flow UL receives the output from the electrical and electronic units 16 heat and this via the plate heat exchanger 51 in the hermetically separated supply air flow ZL and thus in the optionally heated by the Nachheizregister or the heat exchanger 8 supply air ZL "fed into the interior of the tower 10.

The optimized air treatment device 5 does not necessarily have to be arranged in the region of the aggregate module 15, but can be arranged at any other location, in particular because a targeted introduction of air into the unit module 15 and air extraction from the unit module 15 can be generated by air ducts. Also, the supply air duct 74 entered in FIG. 10 does not necessarily end at the upper deck of the unit module 15, but can also be extended beyond that into the interior of the tower 10.

The air treatment device 5 shown in Fig. 11 as an air flow and system schematic and in Fig. 12 in a longitudinal section through a corresponding air conditioner shows a housing 50 with an outside air opening for intake outside air AL, a supply air / pressure opening for delivering the heated supply air flow ZL to the part of the tower 10, which lies above or outside the aggregate module 15, and an exhaust / return air duct or channels 76 and a circulating air / supply air duct or channels 75, via which the circulated air is led into and out of the unit module 15. In the housing 50 of the air treatment device 5, a plate heat exchanger 51 is arranged with hermetically separated, in heat exchanging connection flow paths, of which the first flow path from the vicinity of the tower 10 via the air inlet opening 14 sucked outside air AL via an evaporator or cooler 53, the plate heat exchanger 51, a condenser or a reheat register 55 and the supply air / overpressure opening and the supply air duct 74 to the upper part of the tower 10, during the heat-exchanging connection with the first flow path stationary second flow path through a circulating air fan 56, is conducted in a closed circuit from the unit module 15 via the exhaust air / return air duct 76, the plate heat exchanger 51 and the circulating air / supply air duct 75 into the unit module 15 and the heat energy absorbed by the heat output of the electrical and electronic units 16 over the plate heat exchanger 51 outputs to the first flow path. The first flow path leads via the supply air duct 74, excluding the unit module 15, the heated supply air ZL with overpressure to the interior of the tower 10 and the nacelle 11.

In order to set the number of plates of the plate heat exchanger 51, which are used in the fresh air supply air flow for energy exchange or to be passed on the energy exchange, the plate heat exchanger 51 at the entrance of the cooled outside air AL 'bypass flaps 52 on the adjustment thus influence the energy exchange and thus on the temperature and / or humidity behavior of the air treatment device 5 can be taken. Thus, the bypass flaps 52 of the plate heat exchanger 51 can be included in a temperature and humidity control of the optimized air treatment system 6. Not shown in FIGS. 11 and 12 is the outside air fan 25 according to the embodiments described above. This can be arranged on the pressure side of the optimized air treatment system 6 if, for example, it is part of the air treatment device 2 or 2 'or 2 "and the optimum air treatment device 5 is retrofitted, however, the arrangement of the outside air ventilator 25 on the suction side offers advantages , ie in the flow direction of the outside air AL to the supply air ZL behind the air treatment device 5, since it is here in dry, salt-free air, whereby the risk of corrosion is significantly reduced and only small demands on the material quality of the outside air fan 25 are to make allows the arrangement of the outside air fan 25 on the suction side placements of the outside air fan 25, which are possible and suitable from the unit module 15 over all intermediate decks of the tower 10 to the nacelle 1 1 as a site.

Since the offshore wind energy system 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 an icy wind flows against the tower 10 and the tower 10 is heated on the south side by solar radiation. In order to eliminate or at least reduce the risk of condensation within the entire tower 10, the air treatment device 5 comprises the dehumidifying heat pump formed by the evaporator or cooler 53 and the condenser or reheat register 55 and a compressor 54, which is designed such that a Dehumidification by 1 g / kg air or more is achieved. Subsequently, the temperature of the outside air AL 'increases after passing through the plate heat exchanger 51 to a correspondingly higher temperature in a favorable range of relative humidity, i. as far away from the dew point as possible.

A dehumidification of 1 g / kg already causes, when cooling down the supply air ZL blown into the interior of the tower 10 on the way to the outlet opening 13 in the nacelle 1 1 on the value of the outside air temperature, the dew point line, ie the line 100% humidity in Mollier-h, x-diagram, is not reached, so that there is no risk of condensation inside the tower 10 and the nacelle 1 1. Higher dehumidification than 1 g / kg, for example by arranging an additional electric heater, causes the distance from the dew point line in the Mollier-h, x diagram is further increased, but causes additional energy costs. According to FIG. 11, therefore, the outside air is additionally heated immediately after exiting from the plate heat exchanger 51 with the energy from the dehumidification process via the condenser or the reheat register 55, which in turn has an even more favorable, namely a lower value in the relative Moisture causes. The Mollier-h, x-diagram shown in FIG. 19 shows that the air flowing through the tower 10 and the nacelle 11 and cooled again via the tower walls, even with a one hundred percent cooling effect, reaches the low level achieved by this process Dew point can not fall below. At best, the cooling air flow can rise to a relative humidity of 80% at most.

Since weathering effects can produce the entry points in such a way that the recirculating air flow UL within the plate heat exchanger 51 reaches the dew point and precipitates 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 means that the partial pressure always causes a favorable flow to the area of lower pressure, that is, from the unit module 15 to the tower 10.

The arrangement of the evaporator 53 and condenser 55 is not necessarily required at the air inlet or outlet of the plate heat exchanger 51, but may also be located somewhere within the duct system of the injected into the tower 10 Zuluftstromes ZL, d. h., Are provided within the supply air duct 74.

If the condenser 55 is not arranged in the flow direction after the plate heat exchanger 51, but, for example, immediately after the evaporator 53, then the dehumidification purpose, d. h., the moisture reduction in the same way. 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 described above with reference to FIGS. 5 to 9 described improved air treatment device 4 provides with respect to the functions dehumidifying, reheating, desalting, avoidance of

Condensation throughout the wind energy plant, reducing corrosion and Emergency heating in the case of plant standstill by the dehumidification heat pump system already represents a significant improvement of the conventional dehumidification and desalination by means of the air treatment unit or desalination unit 2, without high investment costs for the improved air treatment unit 4. In particular, in the case of the improved air treatment unit 4, in comparison to the above 10 and 11 described above with reference to FIGS. 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 unit module 15 and an air treatment device with heat recovery system (plate heat exchanger) 51 omitted , so that in the improved air treatment system 4 no targeted air flow through air ducts 75, 76 in the unit module 15 and thus no ielte cooling and 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 is given. In the improved air treatment system 4, the unit module 15 and the interior of the tower 10 and the nacelle 11 form a unit with respect to the air space.

However, the optimum air handling systems 6 shown in FIGS. 10 to 29 may include air handling and dynamics elements and components in the tower 10, such as the arrangement of nozzles, heaters, other re-generation fans, and the like, also in conjunction with the above described improved air treatment device 4 are used.

There is also a cooling of the heat-emitting electrical and electronic units 16 in the unit module 15 with free flow of the 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 arranging the plate heat exchanger 51 in the optimum air treatment device 5, a hermetic separation of the outside air supply air flow, which is separated from the air inlet opening 14 through the supply air duct 74 from the unit module 15 through the interior 100 of the tower 10 and the nacelle 11 to the air outlet opening 13, guaranteed by the circulating air flow, which is guided via the air ducts 75, 76 in the individual floors of the unit module 15 and the output from the heat-emitting electrical and electronic units 16 heat dissipated transported. As a result, no residual moisture and no residual salt content can penetrate the aggregate module 15.

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

13 shows a variant of the configuration of the optimal air treatment device 5 with a reheat register 62 arranged in the exhaust air / return air line 76 of the circulating air UL in the form of a condenser, in the case of heating demand in the aggregate module 15, for example in the winter months at low or too low Temperatures and / or emergency operation at standstill of the offshore wind power plant, is switched by the capacitor 55, so that the dehumidification heat pump formed by the evaporator or condenser 53, condenser or reheat register 55 and compressor 54 in outside air supply air flow AL / ZL heats the supply air ZL (UL) of the circulating air UL of the second flow path, which is delivered to the unit module 15. The energy for this heating operation is supplied by other offshore wind power plants operated in the network.

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 present in bound particles (as dust, so to speak). In the cold winter months weather conditions can occur, which reach due to low temperatures, in particular (but also by the heating of the air) humidity values, which are below 40%. In order to prevent uncleaned air or air having an inadmissibly high salt content from entering into the unit module 15 as a result of leaks or other circumstances, an embodiment of the air treatment device according to FIG. 14 can be used, in which, in addition to the plate heat exchanger 51, the evaporator / Cooler 53, compressor 54 and con- densator / reheat register 55 composite dehumidification heat pump, the high-performance filter 57 and the recirculation fan 56 another high-performance filter 61 is used in the circulating air flow UL, with the salt particles, which could not be completely eliminated in the first treatment stage, additionally deposited.

FIG. 15 shows a schematic longitudinal section through the housing 50 of the air treatment device 5 illustrated in FIG. 14 as an air-guiding and system diagram.

In order to lower the air resistance, which is caused by the arrangement of the high-performance filter 61 in the circulating air flow UL in the air treatment device 6 and thus the energy consumption of the air treatment device 5, the high-performance filter 61 in the embodiment of the air treatment device of FIG. 16 in a bypass 60 to optional switching on or off, for example, depending on the humidity arranged. The bypass 60 has two shutter flaps 602, 603 which, depending on a moisture measurement, determine the proportion of the circulating air flow UL, which is conducted via the bypass channel 601 and thus through the high-efficiency filter 61.

A similar bypass can also be provided in the flow path of the outside air supply air flow in the flow direction behind the plate heat exchanger 51 in conjunction with the high-performance filter 57.

The embodiment of an optimum air treatment device 5 shown in FIG. 17 differs from the air treatment device 5 according to FIG. 14 in that the dehumidification heat pump has two capacitors or reheat registers 55 and 59, of which a first capacitor 55 in FIG Flow direction of the outside air supply air flow in front of the plate heat exchanger 51 and the second capacitor 59 is arranged in the flow direction of the outside air supply air flow to the plate heat exchanger 51. By switching from the first capacitor 55 to the second capacitor 59 or by gradual connection of the second capacitor 59 to the first capacitor 55, the supply air flow ZL can be further heated after the plate heat exchanger 51.

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

Another possibility for temperature control is to provide the recirculation fan 56 with a regulated drive, so that it can promote infinitely variable air volumes. A reduction of the air volume of the circulating air flow UL has the consequence, for example, that less energy is transferred through the plate heat exchanger 51 to the outside air supply air flow. Thus, the air treatment device 5, in addition to the bypass flaps 52 on the plate heat exchanger 51 and the mutually controllable capacitors 55, 59, a further influencing variable for temperature and humidity control.

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

The mode of operation of the air treatment device according to FIG. 18 during summer and winter operation will be explained with reference to the Mollier-h, x diagram shown in FIG. 19. The numeral 1 indicates the humidity and temperature conditions of the outside air in summer, the numeral 2 of the return air or circulating air in summer, the numeral 3 of the outside air in winter and the numeral 4 of the return air / circulating air in winter.

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 takes place both for the outside air AL and for the circulated air UL (reheat) through the condenser 55 or 59 according to the dehumidification heat pump principle. In the third step takes place for the outside air AL further heating by the heat transfer from the warmer, guided over the plate heat exchanger 51 circulating air flow UL. At the same Tig takes place in the third step for the circulating air flow UL, which is in the relatively dry range, that is below or around the 40% relative humidity line, the filtering and thus the elimination of salt particles from the recirculating air flow UL. In the fourth step, the filtering and elimination of the salt particles from the outside air supply air flow takes place after the outside air flow has absorbed heat from the transfer of the plate heat exchanger 51.

The Mollier-h, x-diagram according to FIG. 19 shows that the outside air supply air flow both in summer and winter operation respectively reaches and even falls below the relative minimum moisture content of less than or equal to approximately 40%, which is the The prerequisite for this is that salt particles are formed from the aerosols, which are precipitated in the high-performance filters 57, 61.

Of course, in the arrangement of the air treatment device according to FIG. 18, a division of the arranged in the outside air inlet air condenser in a first capacitor 55 in the flow direction of the outside air before the plate heat exchanger 51 and a second condenser 59 in the outside air supply air behind the plate heat exchanger 51 and arranged in the Alternating operation with the first capacitor 55 analogous to the embodiment of the air treatment device shown in FIG. 17 are operated.

The illustrated in Fig. 20 air guide and system diagram of another embodiment of the optimal air treatment device 5 differs from the embodiment of FIG. 8 by the arrangement of a bypass 70, which leads from Zuluftka- channel 74 and thus from the supply air ZL to the recirculating air UL, where it is connected between the dehumidification heat pump system formed by the evaporator or condenser 62, condenser or reheat register 64, compressor 63 and the high-efficiency filter 61 for overpressure maintenance in the circulating air flow UL.

With this embodiment of the air treatment device 5 it is achieved that the circulating air UL flowing through the unit module 15 is not contaminated by streams from other areas of the wind energy installation with salty air. The required amount of bypass air is very small and does not significantly affect the moisture content of the circulating air UL and only prevents negative flows from the area of the tower 10 of the wind turbine or the air inlet opening 14 in the aggregate module 15 penetrate, so that the required amount of air is only slightly.

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

FIGS. 21 to 27 show further exemplary embodiments of an optimal air treatment device 5 of an optimized air treatment system for normal operation and emergency operation 6, which can be selected adapted to the respective requirements such as environmental conditions, size and power of the wind energy installation, investment costs and the like. The operation common to these embodiments will be described in more detail following the description of the Luftführungs- and system schemes of FIGS. 21 to 27.

The illustrated in Fig. 21 embodiment for an air treatment device 5 differs from the air treatment device of FIG. 20 by the additional arrangement of an independent heater 58, preferably an electric heater, in the supply air flow path ZL behind the plate heat exchanger 51 and in front of the high-performance filter 57 of Air treatment device 5. A bypass 701 branches off from the supply air duct 74 from the supply air ZL to the unit module 15 or optionally via the bypass 702 to the circulating air flow UL, whereby both bypass guides are controlled via a motorized bypass flap 700, so that the supply air portion for overpressure control in the unit module 15 can be regulated , The evaporator 53 of the outside air dehumidification heat pump system preferably has a defrosting device, so that the entire power of the evaporator 53 is provided by two separate evaporator systems.

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

The illustrated in Fig. 23 air guide and system diagram of another embodiment of the invention optimal air treatment device 5 differs from the embodiment shown in FIG. 22 by the optional arrangement of a bypass 71 in the flow path of the circulating air flow UL and a bypass 72 in the outside air supply air Flow path AL / ZL. The bypass 71 in the circulating air flow path UL has bypass flaps 71 1, 712 and a bypass line 713, while the bypass 72 in the outside air supply air flow path AL / ZL contains bypass flaps 721, 722 and a bypass line 723 from the outside air AL to the inlet air ZL.

The bypasses 71, 72 provided in the outside air supply air flow AL / ZL and in the recirculation flow UL make it possible to pass the air streams past the high-performance filters 57, 61 via the bypass lines 713 or 723 if the relative humidity of less than or equal to approximately 40% does not pass can be reached or held. The independently controllable bypass flaps 71 1, 7182 and 721, 722 can be adjusted by a control device in the respective required position, so that the air flows at low humidity either the high-performance filter 57, 61 or via the bypass lines 713, 723 to the high-performance filters 57th 61 are passed by. This ensures that salt crystals, which are produced in the high-performance filters 57, 61 and stored on the "dirty" side, do not decompose again to aerosols at elevated humidity values and penetrate the "pure" side of the high-performance filters 57, 61 and over the increased humidity in the aggregate module 15 or in the tower 10 or the nacelle 1 1 are carried.

The air duct and system diagram of a further embodiment of the optimum air treatment device 5 according to the invention shown in FIG. 24 differs from the air treatment devices described above by the additional arrangement of dehumidification heat pump systems in the outside air supply air flow AL / ZL and in the recirculation air flow UL. That in the flow path of the circulating air stream UL arranged in front of the heating device 65 fed from the waste heat of the electrical and electronic units 16 in the unit module 15 dehumidifying heat pump system consists of the evaporator / condenser 62, compressor 63 and a first capacitor 64. In the outside air supply air flow path from the evaporator / cooler 53rd , the dehumidifying heat pump system consisting of the compressor 54 and a first capacitor / reheat register 55 or a second capacitor / reheat register 59 with mutual operation.

A second condenser / reheat register 66 connected to the dehumidification heat pump system arranged in the circulating air flow UL is assigned to the first condenser / reheat register 65 and can be operated together or alternately therewith. The evaporator 53 arranged in the dehumidification heat pump system of the outside air supply air flow AL / ZL preferably has a defrosting device, for which reason the entire power of the evaporator 53 is applied by two optionally separate evaporator parts.

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

Various variants of a combination of the air treatment device 5 according to FIG. 24 with a conventional air treatment device 2 according to FIG. 2 are illustrated in FIGS. 25 to 27. In the embodiment according to FIG. 25, the conventional air treatment device 2 consists of a first droplet separator 21, a coalescence separator 22 and a second droplet separator 24, which are arranged in the outside air flow AL between the air inlet opening and the optimal air treatment device 5. In this exemplary embodiment, the outside air fan 25 is arranged on the pressure side of the air treatment device 5 between the first droplet separator 21 and the coalescence separator 22.

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

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

In the arrangement according to FIG. 27, the air treatment device 2 only consists of a mist eliminator 21, which is arranged on the suction side of the outside air fan 25, which in turn is arranged on the pressure side of the air treatment device 5. The Koaleszenzabscheider 22 of the arrangement according to FIGS. 25 and 26 has been removed here, since its task is taken over by the air treatment device 5 with.

The components used in the optimized air treatment system 6, such as dehumidification heat pump systems (evaporator, condenser / reheat, heating coil, etc.) can be arbitrarily arranged and combined with each other for functional reasons or due to system or process conditions both in the flow direction before and after the plate heat exchanger 51. 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 in any way with the dehumidification heat pump systems, depending on where the output from the electrical and electronic units 16 heat their best effect achieved by switching and / or step-affected or continuous control. In that regard, the above-described optimized air treatment systems 6 only exemplify some of many possible arrangements.

The optimal air treatment device 5 of an optimized air treatment system 6, which is intended and suitable for both normal operation and emergency operation, shown in FIGS. 10 to 27, has over the simple air treatment device 3 according to FIGS. 3 and 4 and the improved air treatment device 4 according to FIGS. 5 to 9 the following features and functions:

In normal operation, when the wind energy plant is in operation and generates electricity, the outside air AL is transferred from the outside air fan 25 of the conventional air treatment device 2 to the air treatment device 5 and flows through first the evaporator 53, which has the following features or functions:

the evaporator 53 is preferably equipped with a defrosting device, since in the offshore region at low temperatures and high humidity in the freezing point and below there is a risk of icing due to the low evaporation temperature. Deicing devices are known from the dehumidification heat pump design and therefore require no further description. In an advantageous embodiment, the evaporator with de-icing function 53 is designed in two parts for a partial load operation;

the evaporator 53 always operates when the inlet temperature, i. the outside temperature, at the dew point line, i. at 100% relative humidity, and thus an increased risk of condensation within the wind turbine can occur, a temperature drop along the dew point line and thereby eliminates water. This results in a reduction of the absolute humidity, so that the risk of condensation is dispelled. 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 supplemental heaters on the entire route of the flow path of the supply air to the nacelle 1 1 and within the nacelle 11 even at total Recooling of the supply air flow as a whole or in places by the enormous area of the supply air

Tower 10 the dew point is not reached again and condensation on the velvet flow path can not arise. What is essential here is that in order to achieve this objective, the output size 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 provided from the network fed by the wind energy plant in normal operation, because 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 8kJ. After heating by the condenser or the reheat register 55 and, if appropriate, 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 condensation risk 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 connected to the evaporator 53 and the condenser 55 via piping and controls, and may be inside or outside the airflow.

After the dehumidifying and cooling process, the outside air AL flows through the condenser or the reheat register 55 and is reheated there in a first stage. Subsequently, the outside air flow AL receives further heat energy during the flow through the plate heat exchanger 51, which is discharged from the exhaust air of the circulating air flow UL. In this case, the plate heat exchanger 51 hermetically separates the outside air flow AL from the recirculating air flow UL.

At the outlet of the plate heat exchanger 51, the supply air flow has reached a temperature under normal operating conditions, which is less than or equal to about 40% relative humidity in the humidity range. The saline sols are crystallized by this process and can be deposited by the redesigned high performance filter 57. 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 optimal air treatment devices 5 shown in FIGS. 21 to 27 is provided, which is preferably an electric heater because heating must be provided especially in emergency mode.

In addition, a plurality of heating devices can be provided, which are fed, for example, in normal operation from the waste heat of the electrical and electronic units 16 in the unit module 15, in conjunction with the arrangement of an additional electrical heating device.

The temperature and humidity values can be influenced by means of the plate heat exchanger 51, which is preferably provided with bypass flaps 52, in conjunction with a control device of the optimum air treatment device 5, because variable amounts of energy are available for energy exchange or energy transfer.

The dehumidified and desalinated supply air ZL leaving the high-efficiency filter 59 can be led via the supply air duct 74 through the unit module 15 into the tower 10 and to the nacelle 11, the risk of condensation and increased corrosion within the tower 10 and the nacelle 11 being caused by salzerosols eliminated. Further measures for air treatment and air flow in the tower 10 and in the nacelle 1 1 will be described with reference to FIGS. 28 to 34.

In circulating air flow path through the unit module 15 of the continuously variable recirculation fan 56 promotes the exhaust air flow Ab (UL) and the supply air flow ZL (UL) of the circulating air UL in the circulation. The exhaust air flow Ab (UL) is heated by the heat emission in the unit module 15 arranged electrical and electronic units 16, so that in most cases a humidity state of the circulating air UL is reached, which allows the filtering crystallized Salzerosole. If this is not the case, for example, in winter when the heating in the unit module 15 is already greatly reduced by cooling at the tower walls at extremely low temperatures, then the 40% light path can be achieved by the following two devices or functions:

- First, in a first step, the controllable circulating air fan 56 can be reduced to a reduced volume flow, which is a variable process in Dependent on the temperature and humidity setpoints can be performed. At a lower volume flow both a higher exhaust air temperature and a lower relative humidity of the circulating air UL are achieved;

- As occurs at temperatures around the freezing point and optionally below a strong cooling by the large surface of the tower walls in the unit module 15, an additional heater 65 is provided in the embodiments of FIGS. 21 to 27, for example, from the waste heat of the electrical and electronic units 16 is fed in the unit module 15 and which heats the air of the exhaust air flow Ab (UL) of the circulating air UL in conjunction with a control valve to the required temperature. This device is also provided for safety reasons, so that the temperature does not decrease uncontrollably by external influences and thus the required humidity of less than or equal to about 40% relative humidity can be achieved even in such weather conditions.

After the exhaust air flow Ab (UL) of the circulated air UL has reached the required temperature and has been purified by the high-efficiency fine filter 61 provided in the circulating air flow path, the exhaust air Ab (UL) flows through the plate heat exchanger 51 and indirectly supplies the heat energy to the outside air Supply air flow AL / ZL. The infinitely variable circulating air fan 56 now conveys the circulating air flow UL as the supply air flow ZL (UL) to the unit module 15, optionally into the individual levels of the unit module 15.

Now there is a supply air flow ZL (UL) of the circulating air UL available, but on the other hand also has a sufficient minimum temperature at extremely low outdoor temperatures, so that cooling of the unit module 15 is prevented in the circulating air principle again the waste heat in the unit module 15 arranged electrical and electronic units 16 record by cooling and supply the aggregate module 15 via the supply air duct 75 salt-free, dehumidified supply air ZL (UL).

To meet the different requirements in summer and winter operation, the outside air dehumidification heat pump to a second capacitor, which is arranged in the outside air supply air flow AL / ZL after exiting the plate heat exchanger 51. This second capacitor or reheat register is provided, to the energy from the dehumidification heat pump system by switching between the first capacitor and the second capacitor as a function of the outside temperature and the required Entwärmungsleistung for cooling the arranged in the unit module 15 electrical and electronic units 16 in conjunction with the set for the aggregate module 15 limit to transmit the temperature with the most favorable effect.

As a result of the controllability of the recirculation fan 56, there is the possibility of temperature control, in that a continuous adaptation of the required recirculated air UL and thus the circulation of suitable air quantities takes place by regulation of the circulating air UL circulated by means of the circulating air fan 56.

By variable amounts of air both the outside air AL to supply air ZL and the circulating air UL, the optimized air treatment system 6 depending on the parameters of the outside air, such as outside air temperature, humidity and salinity of the outside air AL and depending on the required in the unit module 15 Entwärmungsleistungen and an emergency heating be significantly affected when the wind energy plant is at a standstill. 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.

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

1. since the arranged in the module module 15 heat emitting electrical and electronic units 16 deliver a high thermal output in the summer, the tower walls in this time have a low cooling effect, the set, individual limit of the air temperature in the unit module 15 is reached, so that it It is more favorable to supply the energy from the dehumidification heat pump process (reheat) to the outside air AL or supply air ZL after exiting from the plate heat exchanger 51, since during transfer of the energy (reheat) before entry into the plate heat exchanger 51 also an energy transfer to the Exhaust air flow from (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 in the unit module 15 arranged electrical and electronic units 16 do not cool sufficiently.

2. In an arrangement after the plate heat exchanger 51 causes the dehumidifying process in the outside air supply air AL / ZL simultaneously a temperature drop in the energy exchange of the plate heat exchanger 51 has a reducing effect on the temperature of the exhaust air flow Ab (UL) of the circulating air UL and thus on has the Enthärmungsleistung in the unit module 15.

3. Since the heat transfer of the plate heat exchanger 51 is determined by the temperature difference, the first condenser is preferably to be used in winter, while the second condenser 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 turbine, the optimized air treatment system 6 realizes an emergency operation, which is given for example in light wind, storm or accident or during maintenance of the wind turbine. For example, studies on the basis of wind and weather data for Heligoland have shown that a wind energy plant is not in operation for more than 2000 hours per year due to weak winds or strong winds. 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 grid provides only limited energy and, as a rule, no waste heat for heating the systems and facilities of the wind power plant.

Since in particular strong wind and storm salty, moist outside air AL from the environment of the wind turbine in particular through leaks in the nacelle 1 1 of the wind turbine in the tower 10 and thus also in the unit module 15 is pressed, it is necessary, the pressure in the interior of the tower 10 and the gondola 11 to maintain. For this reason, the conventional air treatment device 2 is kept in operation with the overpressure generating outside air fan 25 and by means of the optimized air treatment system 6 is additionally ensured that the ange- soaked wet and salty outdoor air AL dehumidified and desalinated by filtering as completely as possible.

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

since the heating devices 58, 65 can not be fed from the waste heat of the electrical or electronic units 16, there is no useful energy exchange in the circulated air and fresh air supply air flows through the plate heat exchanger 51, since there is no heat transfer;

the circulating air fan 56 stands still and does not convey circulating air, so that no circulating air flow flows through the unit module 15;

The outside air dehumidification heat pump is in operation, cools, dehumidifies and heats the outside air flow AL, but can not reach the 40% humidity line in every weather situation;

- For safety and residual reheating with a small amount of energy is preferably an electric heater with feed from the mains switched on and causes an increase in the temperature of the supply air, so that the wetness of 40% is achieved and the crystallized salt through the high-performance filter 57 in the supply air can be deposited.

On the way to the upper part of the tower 10, the supply air flow ZL guided via the supply air duct 74 releases a small proportion of the air volume via the bypass 70 to the unit module 15 for overpressure maintenance and for reducing the moisture content of the circulating air. For this purpose, the bypass flap 700 (Figures 21 to 23) is opened and regulated to a certain, usually small amount of air. The bypass air quantity can preferably also be introduced via the exhaust air of the circulating air flow into the unit module 15, namely via the connection between the bypass and the exhaust air of the circulating air according to FIGS. 21 to 23. Due to the above measures, condensation of the supply air ZL or circulating air UL can occur neither in the unit module 15, nor in the tower 10 or in the nacelle 11.

As stated above, the evaporator 53 of the outside air dehumidifying heat pump, but also the evaporator 62 of the circulating air dehumidifying heat pump can be 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 during normal operation, so that one half of the evaporator makes the cooling and / or dehumidification and the other half is de-iced with a closed butterfly valve by heating gas injection.

This special function is also used when in part-load operation of the outside air volume flow is significantly reduced, which can lead to incomplete evaporation of the refrigerant dehumidification heat pump, so that the risk of liquid leakage on the suction line, which lead by liquid blows to the destruction of the compressor would. In part-load operation, therefore, a refrigeration cycle is not in operation and a butterfly valve is closed, so that the reduced air flow rate flows only over the partial surface of the evaporator and thus ensures that the refrigerant is completely evaporated and liquid shocks are avoided.

In relation to the large tower cross section and the large tower height as well as due to the large volume of air, the amount of fresh air normally introduced into the tower is rather low. The flow behavior and the associated cooling behavior in the tower is therefore to pay particular attention.

If the amount of outside air is introduced into the tower 10 at low speed, even if the heating is observed, then the flow is driven in particular by the thermal, since warmer air is known to rise upwards. Due to the large tower height and the large tower diameter, however, the temperature of the air flow reaching the nacelle 11 can not be controlled. Due to temperature stratification, so-called layers form on the line and due to different temperatures Ren the tower wall, which prevail, for example, on the north side and on the south side with and without solar radiation, develop unwanted secondary currents. 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.

In order to avoid this, the embodiment shown in FIG. 28 of a device for aftertreatment, supplementary air treatment and targeted air guidance of the different air streams in a further supplement to the reheater or heat exchanger 8 according to FIG. 10 has a jet nozzle 80 for blowing the supply air flow ZL into the inlet of the Tower 10 at high speed, which is advantageously located in the center of the tower diameter. As a result, the supply air flow ZL heated in the simple air treatment device 3, the improved air treatment device 4 or optimum air treatment device 5 and possibly in the heat exchanger 8 can be selectively guided into the upper region of the tower 10 and closer to the nacelle 11.

The air jet ZL '"at high speed induces permanent air LS on all sides of the tower 10 along its flow path, tearing open air layers and temperature stratifications and preventing secondary flows.

The most centric arrangement of the jet nozzle 80 avoids deflecting and leaning the flow to the tower wall and thus the so-called Coanda effect. For the introduction of air, a nozzle or diffuser shape is chosen because it keeps the static pressure losses low.

In Fig. 28, the outside air AL, the free supply air flow ZL '"in the tower 10, the exhaust air FL from the nacelle 1 1, the conventional air treatment unit 2 for desalination and pre-dehumidification and the optimal air treatment device 5 for air treatment with plate heat exchanger and dehumidification heat pump, the supply air - Overpressure air duct in the supply air duct 74 through the unit module 15, and the recirculating air UL for targeted extraction possibly with duct system and possibly with volumetric flow controllers and targeted supply air duct with duct system and possibly with volume flow regulators and an optional Wärmetau- shear 8 for heating the Zuluft ZL '"in the tower 10 and the nacelle 1 1 shown. The effect of the optimized air treatment system 6 with the optimum air treatment device will be explained with reference to the Mollier-h, x diagram shown in FIG. 29.

Starting from an outside air with a temperature of about 7 ° C at 100% relative humidity at point P1, the sucked outside air is passed through the evaporator 53 and thereby cooled to about 4 ° C at a constant relative humidity according to the arrow A. In the plate heat exchanger 51 according to FIGS. 4 to 7, the cooled down outside air in the plate heat exchanger 51 by means of the recirculated air in the aggregate module 15 recorded by the electrical and electronic units 16 heat emitted according to the arrow B of 4 ° C to about 21 ⁰ C heated at a relative humidity of 30%. By the subsequent heating or reheating in the condenser 55 of the dehumidification heat pump, the supply air is heated according to the arrow C to about 27 ° C and as supply air via the supply air duct 6 in the upper part of the tower 10, ie, outside the unit module 15 in the interior of the tower 10 and the overhead gondola 1 1 blown. Until reaching the outlet openings 3, the injected supply air is cooled to a maximum of 7 ° C at a maximum of 80% relative humidity according to the arrow D, which ensures that the dew point can not be achieved and condensation can not occur.

At the same time, the circulating air guided in recirculation mode by the unit module 15 according to the point P2 shown in FIG. 29 according to the arrow E as exhaust air return air to the plate heat exchanger 51 with a temperature of 30 ⁰ C and a relative humidity of 40% supplied and in the plate heat exchanger 51 at hermetically cooled relative to the outside air / supply air and overpressure current through the plates heat exchanger 51 to about 15 ° C with increase in relative humidity to about 100% and discharged through the circulating air / supply air opening of the aftertreatment device 5 to the unit module 15.

The arrow F denotes the direction of action of the partial pressure, which causes a reduction of the moisture content in the circulating air flow and thus a drying in the aggregate module 15 and thus a favorable flow always to the range of low pressure, ie from the aggregate module 15 to the tower 10 as described above.

Line G highlights the line of 80% relative humidity. 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. Guiding the sucked from the outside air through an air duct 6 through the unit module 15 through to the lying above the unit module 15 part of the tower 10 and located at the top of the tower 1 1, so that arranged in the unit module 15 electrical and electronic Aggregates 16 do not come into contact with salty air and therefore no contamination of aggregates 16 takes place.

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 unit module 15 via Zuluft- and exhaust air ducts 75, 76 with a hermetic separation of the air streams with simultaneous indirect energy transfer

for the purpose of cooling the circulating air passed through the aggregate module 15,

- For the purpose of heating in the tower 10 and the nacelle 1 1 injected supply air; - For the purpose of dehumidifying the circulating air flow at appropriate temperature differences.

3. An integrated dehumidification heat pump system is the moisture reduction of the outside air and their simultaneous heating with the overall effect that after cooling the outside air in the tower 10, the dew point is not reached or can not be achieved, so that condensation in the tower 10 and in the nacelle. 1 1 is avoided.

4. Targeted supply and return air ducts according to the circulating air principle in the unit module 15 through air ducts 7, 8, which may be provided with additional volume flow controllers in the individual zones or floors of the unit module 15 for optimum air cleaning and targeted heating of the electrical and electronic units 16 whose heat is dissipated through the surfaces of the electrical and electronic assemblies 16. 5. Supplementary reheating of the supply air, preferably with the involvement of a control device, the tower 10 and the nacelle 11 from the waste heat of the electrical and electronic units 16 to prevent condensation in the tower 10 and in the nacelle 11th

6. Arrangement of a high-performance fine filter 61 for further reduction of the salt content of the recirculated air guided through the aggregate module 15 at moisture 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 energy plant and depending on the tower height of the wind energy plant, there are 15 further intermediate decks above the aggregate module, i. Separations in the cross section of the tower 10, provided. As a result, the blown into the interior of the tower 10 by means of the outside air fan 25 induction beam of the supply air on the way to the nacelle 1 1 is interrupted or obstructed on its flow path. Such intermediate decks slow the supply air flow by permanent induction, i. 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 is also driven by the thermal effect upwards towards the nacelle 1 1, cools on the long walls to the nacelle 11 on the tower walls, so that the thermal buoyancy gradually slows down.

On the other hand, intermediate decks, in particular for larger tower heights, offer a good opportunity to maintain or increase the dynamics of the supply air flow by selectively increasing the flow rate of the supply air at a preferably centrically arranged device, which increases the velocity of the supply air flow, such as a nozzle or a diffuser, and a directed flow Reproduced with high induction behavior above each sub-deck. This arrangement can be repeated for each intermediate deck, wherein the speed increasing means is designed such that the beam length reaches the height of the respective next intermediate deck and is picked up and continued there by the next speed increasing unit. This technical solution with the arrangement of a speed increasing device designed as a nozzle or diffuser is carried out without a mechanical auxiliary unit, such as a ventilator, as long as an intermediate deck represents an air-tight partition and the amount of air introduced through the central outside air fan 25 the considerable 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, which extends to the nacelle 1 1 of the wind turbine, so that the required increase in speed can be effected via the built-in nozzles or diffusers or similar devices.

If, however, the intermediate deck according to FIGS. 30 and 31 has gaps at its side edges to the tower wall or openings are provided in the intermediate deck for carrying out an elevator cabin or other facilities, mechanical additional equipment such as ventilators 80, 81, 82 are required in FIG to increase the dynamic speed of the supply air flow ZL, ZL ', ZL ", ZL'", since the introduced via the outside air fan air quantity penetrates all openings due to the large Druckverhal-, resulting in an uncontrolled flow behavior in the tower 10 and the nacelle 1 1 develop can.

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

In order to achieve a targeted flow of the supply air flow and thereby avoid bypass flows through the edge gaps or elevator bushings, it is advantageous that the fans 80, 81, 82, which generate the flow in the central region of the tower 10 again, with a slightly elevated, suitable amount of air, for example, + 10%, interpreted as compared to the supply air, so that by overpressure above the respective intermediate deck and negative pressure below the respective intermediate deck a small amount of air flows through the bypasses and thus prevents uncontrolled air flows from the over-pressure behavior of the outdoor fan 25 arise. The mechanical air conveyors in the form of additional fans 80, 81, 82 are designed with an extremely low static pressure, because the Außenluftventi- vator 25 generates a significant excess pressure, which can only flow in the nacelle 11 after all the way through the tower 10 and finally Only there loses through leaks and pressure flaps as exhaust air FL. The tower 10 is to be regarded as hermetically closed, so that here the excess pressure is maintained until entry into the nacelle 1 1.

FIG. 32 shows the optimized air treatment system 6 for the wind energy installation shown in FIG. 30 in conjunction with the conventional air treatment or desalination apparatus 2 for the pre-dehumidification and desalination of the outside air AL.

As a result of the cooling effect through the tower walls in conjunction with the long flow paths, it proves to be advantageous in connection with the mechanical air conveyor 80, 81, 82 to cool the partial air flow through heaters 8, 83, 84, for example, from the Waste heat is arranged in the unit module 15, heat-dissipating electrical and electronic units 16 is fed to reheat. The temperatures in the entire tower 10 can be made more uniform compared to a single central heating and affect the temperature condensation behavior in the tower 10 advantageous.

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

The solution according to the invention has been described above using the example of an offshore wind power plant with the prevailing in seawater climatic conditions of a moist and salty outside air at seasonal very cold or very warm outside air temperatures. This results in the requirements of dehumidifying and desalination of the outside air and providing a dehumidified and desalinated supply air in the area of the unit module 15, inside the tower 10 and in the nacelle 11 to prevent corrosion and ensure the discharge of the in the aggregate module accumulating heat loads. 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.

Regardless of other harsh environmental conditions, dehumidification and the associated safety against condensation is also significant in land-based wind turbines, as wind turbines have electrical and electronic equipment that is sensitive to excessive humidity levels at which they are subject to increased corrosion , as well as react to impermissibly high temperatures, which can lead to the destruction of the electrical and electronic devices see.

In a modification of the embodiments described above, not all devices must be arranged directly in the tower in such wind power plants, but can also be provided in containers or buildings next to the tower of the wind energy plant. Even at such outbuildings or containers, the dehumidification of the outside air or the prevention of condensation and optionally the heat dissipation of the electrical and electronic units of considerable importance.

As explained in the introduction, the risk of corrosion depends essentially on the climatic conditions at the location of a wind power plant. The measures described above are used to maintain the temperature and humidity values of the air inside the wind energy plant, which are outside the critical humidity. In addition to these, the measures eliminating or at least minimizing the risk of corrosion, however, it should be noted that the electrical and electronic units arranged in the tower and the nacelle of the wind power plant are sufficiently cooled for safe, permanent operation. In certain regions, the case may occur that, although the air is adequately desalinated and dehumidified, the supply air flow discharged into the tower and / or into the nacelle of the wind energy installation has a temperature height that is too high for cooling the units is or is not completely sufficient for cooling. In these cases, the use of an optimized with respect to the cooling air treatment device by way of Zuluftstromes in the tower of the wind power plant or within the nacelle of a wind power plant according to the below-described Fig. 39 to 45 is advantageous.

Fig. 39 shows an air treatment system with a combination of an improved air treatment device 4 with a conventional air treatment or desalination unit 2 "according to FIG. 13 below the dotted line and a plate heat exchanger 91 with separate air flow guide in conjunction with an additional fan 92 above the dotted line The external air AL conditioned by the combination of the improved air treatment device 4 in conjunction with a conventional air treatment or desalination device 2 "is supplied as supply air ZL to the one flow path of the plate heat exchanger 91 and from this as the cooled or indirectly cooled supply air ZL 'to the tower 10 or the aggregate module 15 as shown in FIG. 9 delivered. The other, from the supply air flow ZL-ZL 'hermetically separated air flow leads from the outside air AL via the additional fan 92 to the exhaust air FL.

At a temperature of the supply air flow ZL emitted by the combination of improved air treatment device 4 and conventional air treatment or desalination device 2 "which is insufficient or not sufficient to cool the aggregates, the supply air flow ZL-ZL 'via the plate heat exchanger 91 becomes free, indirect cooling in which the outside air flow is conducted from the outside air connection AL to the outgoing air connection FL via the plate heat exchanger 91 and thereby indirectly cools the supply air flow ZL-ZL 'The two air flows guided through the plate heat exchanger 91 are hermetically separated, so that a contamination of the supply air flow ZL-ZL 'is excluded with salty and humid air.

It is ensured in the interior of the tower 10 and the unit module 15 that the maximum temperature can reach the value of the outside temperature and with respect to the humidity can not exceed the value of 65% relative humidity. The targeted dehumidification by means of the combination of improved air treatment device with conventional air treatment or desalination apparatus according to FIG. 13 ensures that the dew point is never reached at any time and at any location within the tower 10, so that a secure corrosion protection even under consideration linear increase in corrosion rate at humidity levels greater than 65% relative humidity is achieved.

As an alternative to the combination of improved air treatment device 4 and conventional air treatment or desalination device 2 "according to FIG. 13, it goes without saying that a combination of improved air treatment device 4 and conventional air treatment or desalination device 2" according to FIG. 12 or an arrangement according to FIGS. 15 to 31 are used, the latter being more suitable for special cases because of the increased equipment expense.

The air treatment system illustrated in FIG. 39 with a combination of improved air treatment device 4 with a conventional air treatment or desalination device 2 "in conjunction with a plate heat exchanger 91 for indirect free cooling of the supply air ZL 'discharged into the tower 10 or into the aggregate module 15 serves in FIG primarily the cooling of the supply air ZL 'for sufficient cooling or heating of the electrical and electronic units arranged in the tower 10 or in the nacelle 11. However, since in the winter months only through the tower walls a strong cooling within the tower 10 The fans 25, 92 arranged in the air treatment system according to FIG. 39 are preferably equipped with controllable drives to ensure a constant temperature with targeted temperature increase and constant maintenance, so that via the volume flow the cooling or the use of the waste heat for tower heating inwinter months can be regulated from 0 to 100%.

40 shows the air treatment system according to FIG. 39 with an additional mechanical cooling device consisting of a compressor 930, an evaporator or radiator 931 and a condenser 932. This modified air treatment system for a wind power plant is preferably used for installation in climatic zones, the higher ones Outdoor temperatures that are insufficient for a free, indirect cooling. In this air treatment system, the free, indirect cooling is used in a first sequence and depending on the season or demand, the mechanical cooling system 930, 931, 932 in a second sequence targeted or regulated switched. In this arrangement too, the fans 25, 92 are equipped with controllable drives for generating variable volumetric flows as a function of the temperature. Fig. 41 shows a schematic representation of a device that can be used in sub-areas of the wind power plant 1 for additional, or complementary or independent cooling of aggregates, such as the transmission and the generator in the nacelle 11 of the wind energy plant 1 ,

The device for additional cooling of units comprises a plate heat exchanger 94 with separate, but in heat-exchanging connection air flow guides an outside air flow, which leads from an outside air connection AL to a continuous air connection FL via a first fan 95, and a recirculation air flow from a supply air connection ZL 'leads to a supply air connection ZL "via a second fan 96. The first fan 95 conveys outside air AL via the plate heat exchanger 94 to the exhaust air FL and thereby cools the hermetically separated recirculating air flow ZL'-ZL" to use the free, indirect cooling the second fan 96 is conveyed.

Also in this arrangement, the fans 95 and 96 are equipped with controllable drives to achieve variable volume flows as a function of the temperature.

The device illustrated in FIG. 42 differs from the device according to FIG. 41 in the arrangement of an additional mechanical cooling with a compressor 970, an evaporator 971 and a condenser 972. This device is used to set up the wind power plant in climatic zones, have the higher outside temperatures, which are not sufficient for a free, indirect cooling, so that the mechanical refrigeration system 970, 971, 972 can be switched on for additional mechanical cooling. Analogous to the air treatment system according to FIG. 41, the free cooling is used in the first sequence and the mechanical cooling system 970, 971, 972 is activated in a targeted or regulated manner in a second sequence depending on the season or demand.

Also in the device according to FIG. 42, the fans 95 and 96 are equipped with controllable drives in order to achieve variable volume flows as a function of the temperature.

43 shows a schematic representation of a wind power plant 1 with a tower 10 and a nacelle 11, in which the air treatment systems LBS and E are arranged with supplementary cooling devices or cooling devices according to FIGS. 39 to 42. Analogously to the arrangement according to FIG. 9, the modified air treatment system LBS according to FIG. 39 or 40 is used in the lower part of the tower 10, which supplies a supply air flow ZL 'to the inside of the tower cooled down as required and regulated

10 or to the aggregate module 15 according to FIG. 9. If additional cooling is required, a device E according to FIGS. 41 or 42 is provided in the nacelle 1 1, which cools the air within the nacelle 1 1 by using an additional outside air flow from the outside air connection AL to the exhaust air connection FL.

The arrangement according to FIG. 43 is only to be understood as an example. For example, the device E for additional, independent cooling of aggregates in the nacelle

1 1 of the wind energy system omitted if the modified air treatment system LBS in the lower part of the tower 10 a sufficiently cooled supply air flow ZL 'emits, so that the temperature in the nacelle 11, taking into account the heat output of the units arranged there, such as gear and generator, a specified value does not exceed.

FIG. 44 shows, on a temperature example for the area of the German North Sea, the effect of the modified air treatment systems in the tower 10 and in the nacelle 11 of the wind power plant 1. The modified air treatment system LBS in the lower part of the tower 10 draws in outside air with a flow velocity of 10,000 m ³ / h at a temperature of 20 ⁰ C and a relative humidity of 90%. The combination of an improved air treatment device with a conventional air preparation or desalination apparatus according to FIG. 13 supplies a supply air flow ZL at a flow rate of 5,000 m ³ / h at a temperature of 40 ^° C. and a relative air humidity of 30% to one Flow channel of the plate heat exchanger, through which also a part of the outside air flow is hermetically separated from the supply air flow ZL at a flow rate of 5,000 m ³ / h at a temperature of 20 ⁰ C and a relative humidity of 90% to the exhaust port FL is passed. The supply air ZL 'cooled down by means of the plate heat exchanger is delivered to the unit module or the interior of the tower 10 at a flow rate of 5,000 m ³ / h at a temperature of 27.4 ° C. and a relative air humidity of 60%. This supply air flow ZL 'enters the nacelle 11 and can be further cooled down there if necessary in the recirculation mode.

It is considered that the steel tower with its large steel mass causes a high cooling of the flowing air and thus a positive effect on the cooling which has upwardly flowing air. This cooling effect is used. Based on the above-mentioned temperatures and a maximum permissible temperature in the nacelle of 40 ⁰ C would at a temperature difference of .DELTA.K = give 1 1 ° and a flow of 5.000 m ³ / h a Heat dissipation of approximately 18 kW. This means that the total heat load in the nacelle 11 of, for example, 35 kW can be reduced by this value. The residual cooling power could then be done with a much smaller Entwärmungsgerät with a power of about 20 kW, so that a flowing from bottom to top air flow for the following reasons is preferable:

1. The cooling effect of the steel tower 10 benefits the heat balance,

2. The cooling of the nacelle 11 is favorably influenced.

3. A reduction of the Entwärmungsgerätes is possible in considerable size, so that a smaller unit, smaller air ducts, smaller ventilation holes in the outer skin of the tower 10, better Reguliermöglichkeiten in summer and winter operation, better temperature management (temperature increase in the entire interior of the wind energy plant ) at low outside temperatures, reduced power consumption by smaller motors, which is significant for the standstill and low load times of the wind power plant, cost reduction in terms of investment and operation are achieved and the continuous and complete flow through the entire wind energy plant critical Excludes points of condensation.

Fig. 45 shows a schematic representation of a method for increasing the cooling effect through the tower walls.

Since in the lower part of the tower 10 units, such as transformers, converters and switchgear are installed, which cause an increase in the air temperature through heat dissipation, the introduced, dehumidified and desalinated outside air absorbs this heat and flows up into the nacelle 11 In the nacelle 1 1 are again aggregates such as transmission and generator, which also give off heat or require cooling. For this reason, it is necessary that the upwardly flowing and already heated air is sufficiently cooled in order to have in the nacelle 1 1 on the necessary cooling effect for the units set up there. The big steel mass of the Turmes 10 offers an excellent opportunity for this, but the cooling effect is low when the upflowing current reaches the nacelle 11 by spinning.

A significant improvement occurs when the heat transfer coefficient is improved by mechanical means. This is achieved by an air conveyor which selectively generates an increase in speed by nozzle action, produces in conjunction with the Koanda effect an eddy current in the entire tower and increases the heat transfer coefficient. Depending on the particular climatic zone, in which the wind energy plant is set up, this device can be dispensed with, if desired, entirely without additional cooling in the nacelle 11, but at least a supplementary mechanical cooling device can be made substantially smaller.

To increase the cooling effect through the tower walls, a speed-increasing device, for example an air-conveying device in the form of a fan and a nozzle, is arranged at the starting point S according to FIG. 45. The nozzle may have any geometric shape, for example a round shape or a flat-jet shape. Also, depending on the tower height and / or the tower diameter, one or more further nozzles or devices can be arranged.

The device is arranged so that the air is driven at high speed obliquely upward, sharply up the tower wall. Taking advantage of the Koanda effect, the blown-in air stream virtually sticks to the tower wall and generates a rotary movement (vortex flow) throughout the tower 10, which tears open the air layers and air layers and ensures that this movement results in better contact with the tower wall and thus the Cooling effect is significantly improved. In particular, the thermal boundary layers are torn open and the heat transfer is substantially improved, that is to say a marked improvement in the heat transfer coefficient is achieved, since the intensity of the heat transfer at the boundary surface becomes considerably stronger. _{l C} N

LIST OF REFERENCE NUMBERS

1 offshore wind energy plant

Air treatment or desalination device

3 Simple air treatment device

4 improved air treatment device

5 Optimum air treatment device

6 Optimized air treatment system

8 heating device

10 tower

1 1 gondola

12 rotor blades

13 outflow openings

14 air inlet opening

15 aggregate module

16 electrical and electronic components and units

21 First droplet separator

22, 23 Coalescence separator

24 second droplet separator

25 outside air or overpressure fan

31 heating device or air heater

32 high-performance filters

41 evaporator

42 compressor

43 condenser or reheat coil

44 high-performance filters

50 housings

51 Air treatment unit with recuperative heat recovery system

(Plate heat exchanger)

52 bypass flaps

53 evaporator or cooler

54 compressor

55 capacitor or reheat register

56 Recirculation fan

57 High-performance filter in outdoor air supply airflow

58 heating device 59 second capacitor

60 bypass

61 high-performance filters in the recirculating air stream

62 evaporator or cooler

63 compressor

64 capacitor or reheat register

65 heating device

66 Second capacitor / reheat register

70, 71, 72 Bypass

74 supply air duct

75, 76 circulating air ducts

80 jet nozzle

81, 82 fans

83, 84 heaters

91, 94 plate heat exchanger

92 additional fan

95 first fan

96 second fan

700 bypass flap

701, 702 Bypass

711, 712 bypass flaps

713 bypass line

721, 722 bypass flaps

723 bypass line

930, 970 compressor

931, 971 evaporator or cooler

932, 972 capacitor

AL outside air

ZL, ZU, ZL "Zuluft

FL exhaust air

UL circulating air

From (UL) exhaust air of the circulating air

ZL (UL) supply air of the circulating air

E, LBS cooling device, air treatment system

Claims

claims

1. A method for air treatment in wind power plants, in particular in offshore wind power plants, with a tower (10), at the upper end of a gondola (1 1) with a generator and at least one rotor blade (12) and in the interior heat-releasing 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 which has at least one air inlet opening (14) and an air outlet opening (13) the air inlet opening (14) from the environment of the tower (10) moist and saline outside air (AL) is sucked,

characterized,

the moist and saline outside air (AL) drawn in via the air inlet opening (14) from the surroundings of the tower (10) is heated until a predetermined relative humidity of the outside air (AL) is reached, at which the outside air (AL) is contained. Salzaerosols are at least partially crystallized, that crystallized

Salzaerosole and in the outside air (AL) contained salt particles are deposited.

2. The method according to claim 1, characterized in that via the Luftein- outlet opening (14) from the environment of the tower (10) sucked moist and saline outside air (AL) in an air treatment device (4) cooled and thereby the absolute humidity of the outside air (AL) is lowered, that the cooled and dehumidified outside air (AL) is heated until a predetermined relative humidity of the outside air (AL) is reached, in which the salt aerosols contained in the outside air (AL) are at least partially crystallized, that crystallized Salzaerosole and in the

Outside air (AL) contained salt particles are deposited.

3. The method according to claim 2, characterized in that via the air inlet opening (14) from the environment of the tower (10) sucked moist and salt-containing outside air (AL) is heated until a predetermined relative humidity of the outside air (AL) is reached in which the salt aerosols contained in the outside air (AL) are at least partially crystallized, that the crystallized salt aerosols and salt particles contained in the outside air (AL) are separated and that the dehumidified and desalinated outside air (AL) indirectly, freely cooled and as a cooled supply air (ZL ') to the interior of the tower (10) and / or to the unit module (15) is discharged.

4. The method according to claim 3, characterized in that for the indirect, free cooling of the supply air (ZL ') a hermetically separated from the supply air flow (ZL-ZL'), but in good heat-conducting contact with the supply air flow (ZL-ZL ') standing air flow from the outside air (AL) to the exhaust air (FL) is used.

5. The method according to claim 3 or 4, characterized in that the indirectly, freely cooled down supply air (ZL ') is further cooled with a mechanical cooling device prior to delivery to the interior of the tower (10) and / or to the unit module (15) ,

6. The method according to claim 2, characterized in that the dehumidified and desalinated outside air (AL) as supply air (ZL) to the interior of the tower (10) and / or to the unit module (15) is discharged.

7. The method according to claim 6, characterized in that the cooled and dehumidified outside air (AL) is heated until the relative humidity of the outside air (AL) is less than or equal to 40%.

8. The method according to at least one of the preceding claims, characterized in that the heated outside air (AL) filtered and the crystallized salt aerosols and in the outside air (AL) contained salt particles are deposited.

9. The method according to at least one of the preceding claims, characterized in that via the air inlet opening (14) from the environment of the tower (10) sucked moist and salty outside air (AL) or the cooled and dehumidified outside air (AL) with energy from the Waste heat of the heat-emitting electrical and electronic units (16) is heated.

10. The method according to claim 9, characterized in that via the air inlet opening (14) from the environment of the tower (10) sucked moist and salty outside air (AL) or the cooled and dehumidified outside air (AL) of a

Air treatment device (5) is supplied with separate flow paths, in a recirculating air flow (UL) which is in heat-exchanging connection with the outside air (AL) is guided in a closed circuit through the aggregate module (15) and the heat energy absorbed by the heat emission of the electrical and electronic units (16) is transferred to the outside air (AL) emits, from the under exclusion of the aggregate module (15) heated supply air (ZL) with overpressure to the

Interior of the tower (10) and the nacelle (1 1) is discharged.

1 1. A method according to claim 10, characterized in that the volume flow of the outside air (AL) and / or the recirculating air (UL) independently generated and for adjusting the heat transfer in the unit module (15) and / or the temperature or humidity of the supply air ( ZL) are controlled and regulated.

12. The method according to claim 10 or 11, characterized in that the outside air (AL) via a dehumidifying heat pump (41 - 44; 53-55, 59) with an outdoor ßenstromstrom (AL) arranged evaporator (41; 53), compressor (42; 54), condenser or Reheatcoil (43; 55) and high-performance filter (44; 59) is performed.

13. The method according to at least one of the preceding claims 10 to 12, characterized in that the air treatment device (5) contains a Luftbehand- treatment device with heat recovery (51) through which the hermetically separated flow paths of the outside air supply air flow (AL / ZL) and in that the dehumidifying heat pump (53-55; 59; 63) has at least one condenser or reheat register (55, 63) which is located in the flow direction of the outside air supply air flow (AL / ZL) upstream of the air treatment system. advises 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.

14. The method according to claim 13, characterized in that the dehumidifying heat pump (53-55, 59, 63) has 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 heat recovery air treatment unit (51) and the second condenser (63) in the flow direction of the outside air supply air flow (AL / ZL) after the heat recovery air treatment unit (51) is arranged, and that by switching from the first capacitor (55) to the second Con- capacitor (63) or by stepwise connection of the second capacitor (63) to the first capacitor (55) of the supply air (ZL) is further heated.

15. The method according to claim 13 or 14, characterized in that the proportion of the guided through the air treatment unit with heat recovery (51) outside air supply air flow in dependence on a temperature and / or humidity control of the optimized air treatment system (6) is set.

16. The method according to at least one of the preceding claims 10 to 15, characterized by at a Umluftströmungsweg (UL) arranged capacitor

(62), which is switched to when heating is required in the unit module (15).

17. The 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 the from the evaporator or cooler (62), capacitor or reheat register (64),

Compressor (63) and high-performance filter (61) formed Entfeuchtungswärmepumpensystem in the recirculating air flow (UL) for overpressure in the circulating air flow (UL).

18. The method according to claim 17, characterized in that a flap system (640, 700) connects or bypasses the bypass via a moisture measurement.

19. The method according to at least one of the preceding claims, characterized in that the air treatment device (5) emitted Zuluftstrom (ZL) via a heat exchange device (8) is guided, the heat from the heat of the electrical and electronic units (16) recorded Heat energy to the supply air flow (ZL) depending on the air temperature in the interior of the tower (10) and the nacelle (11) emits.

20. The method according to at least one of the preceding claims 10 to 18, character- ized in that the supply air (ZL) at least in the section between the air treatment device (5) and the entrance into the interior of the tower (10) in a supply air duct (74 ) to be led.

21. The method according to at least one of the preceding claims, character- ized in that the air treatment device (5) discharged supply air (ZL) additionally dehumidified and heated with the energy obtained from the dehumidification process prior to delivery to the interior of the tower (10).

22. The method according to at least one of the preceding claims 10 to 15, character- ized 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.

23. The method according to at least one of the preceding claims, character- ized in that via the air inlet opening (14) from the environment 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.

24. The method according to at least one of the preceding claims, character- ized 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 in terms of flow, the preferably a first droplet separator (21) for gross pre-separation of rain, spray and the like, a Koaleszenzabscheider (22, 23) to form larger droplets, a second droplet separator (24) as a Nachabscheider for intercepting and separating the previously formed droplets and the required air flow generating outside air fan (25).

25. The method according to at least one of the preceding claims, character- ized in that with additional cooling demand in parts or areas of the wind power plant (1) an indirect, free cooling of the circulating air (UL) by means of a ßenluftanschluss out to the exhaust port additional Outside air flow (AL), which is hermetically separated from the recirculation air flow, but in good thermal contact with the recirculating air flow (UL) is.

26. The method according to at least one of the preceding claims, characterized in that the supply air (ZL, ZL ', ZL ") is processed in such a way that the dehumidified to the interior of the tower (10) and / or to the unit module (15) and desalinated supply air (ZL, ZL ', ZL ") does not reach the dew point again on cooling down to the value of the outside air and performance maintains a maximum relative humidity of less than 60% relative humidity.

27. The method according to at least one of the preceding claims, character- ized in that the processed supply air (ZL, ZL ', ZL ") at high speed obliquely upward, sharp on the tower wall along up in the tower (10) is blown in such a way in that the blown-in air flow is moved along the tower wall and produces a rotary movement (turbulent flow) in the tower (10), which tears up air layers and air layers.

28. A device for air treatment in wind energy systems, in particular in offshore wind energy systems, with a tower (10), at the upper end of a gondola (1 1) with a generator and at least one rotor blade (12) and in the interior heat-releasing 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 at least one air inlet opening (14) and an air outlet opening (13), wherein the air inlet opening (14) moist and saline outside air (AL) is sucked in from the environment of the tower (10),

marked 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 Salzaerosols crystallized into particles in the outside air (AL) or desalinated and dehumidified outside air (AL ') and for the delivery of heated supply air (ZL) via the aggregate module (15) into the tower (10) and into the nacelle (11).

29. A device for air treatment in wind energy systems, in particular in offshore wind energy systems, with a tower (10), at the upper end of a gondola (1 1) with a generator and at least one rotor blade (12) and in the interior heat-releasing electrical and electronic units (16), such as switchgears, switching devices, transformers, frequency converters and the like, being arranged in an aggregate module (15) of the tower (10) and having at least one air inlet opening (14) and one air outlet opening (13), wherein over the air inlet opening (14) from the environment of the tower (10) moist and salty outside air (AL) is sucked in,

marked by

an air treatment device (4) with one of an evaporator (41) for reducing the absolute moisture content of the supplied outside air (AL) or desalted in an upstream air conditioning or desalination device (2) 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 deposition.

30. A device for air treatment in wind power plants, in particular in offshore wind energy systems, with a tower (10), at the upper end of a nacelle

(1 1) 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 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 environment of the tower (10) moist and salty outside air (AL) is sucked in,

marked 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 via the air inlet opening (14) sucked outside air (AL) to the interior of the tower (10 ) with the exception of the unit module (15) discharged supply air (ZL) leads and the second flow path in recirculation mode supply air to the unit module (15) and sucks exhaust air or return air from the unit module (15).

31. The device according to claim 30, characterized in that the air treatment device with recuperative heat recovery system includes a plate heat exchanger (51) in the flow direction of the first flow path according to a with the air inlet opening (14) connected air treatment device (2) for desalination of the sucked outside air (AL) is arranged.

32. Apparatus according to claim 31, characterized in that the plate heat exchanger (51) on the inlet side of the cooled outside air (AL ') adjustable

Bypass flaps (52).

33. 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.

34. Device according to claims 30 to 33, characterized by a supply air duct (74) from the air treatment device (5) to the unit module (15) separated from the interior (100) of the tower (10).

35. Apparatus according to claim 29, characterized in that the output of the air treatment device (4) is connected to a first flow path of an air treatment device (91) with recuperative heat recovery system and hermetically separated first and second flow paths, wherein the first flow path at the outlet of the air treatment device (4) discharged supply air (ZL) as cooled down supply air (ZL ') to the interior of the tower (10) and / or the aggregate module (15) and in the second flow path outside air (AL) by means of an additional fan (92) sucked and on an outgoing air connection is delivered.

36. Apparatus according to claim 35, characterized in that in the flow path of the supply air (ZL) to the cooled supply air (ZL '), a mechanical refrigeration device (930 to 932) is arranged.

37. Apparatus according to claim 29, characterized in that the supply air duct (74) is connected to a heat exchanger (8) which emits heat energy absorbed by the electrical and electronic units (16) to the supply air flow of the first flow path leading into the interior of the tower ,

38. Apparatus according to claim 37, characterized in that the heat energy emitted by the heat exchanger (8) to the supply air flow in dependence on the temperature in the interior of the tower (10) and / or the nacelle (11) is adjustable and that at least one of the temperature in the interior of the tower (10) and / or the nacelle (11) detecting temperature sensor is connected to a control device.

39. The device according to at least one of the preceding claims 30 to 38, characterized in that the circulating air (UL) in supply air and exhaust air ducts (75, 76) to the unit module (15) and from the unit module (15) is guided

40. The device according to at least one of the preceding claims 30 to 39, characterized in that in the circulating air flow path (UL), a further high-performance filter (61) is arranged.

41. Device according to claim 40, characterized in that the further high-performance filter (61) is arranged in a bypass (60) with two shutter flaps (602, 603), the position of which determine the proportion of the circulating air flow (UL) as a function of a humidity measurement which is passed through the high-efficiency filter (61) arranged in the bypass channel (601).

42. The device according to at least one of the preceding claims 30 to 41, characterized in that the circulating air fan 56 for continuously variable delivery of circulating air has a regulated drive.

43. Device according to at least one of the preceding claims 30 to 42, characterized in that both in the outside air supply air flow (AL-ZL) from an evaporator or cooler (53), condenser or reheat register (55) and compressor ( 54) existing Entfeuchtungswärmepumpensystem and in the circulating air flow (UL) from a vaporizer or cooler (62), condenser or reheat register (64) and compressor (63) existing and in the exhaust duct (76) of the circulating air

(UL) arranged in the flow direction in front of the high-performance filter (61) arranged Entfeuchtungswärmepumpensystem.

44. Device according to at least one of the preceding claims 30 to 43, characterized by a branching off from the supply air duct (74) and with the circulating air

Flow path (UL) between the evaporator or cooler (62), condensate sator or reheat register (64), compressor (63) and the high-performance filter (61) formed Entfeuchtungswärmepumpensystem in the circulating air flow (UL) extending bypass (70) for overpressure retention in the recirculation air flow path (UL)

45. The device according to at least one of the preceding claims 30 to 44, characterized in that in the supply air flow path (ZL) of the air treatment device (5) behind the plate heat exchanger (51) and in front of the high-performance filter (57) an independent heating device (58), preferably an electric heater, is arranged.

46. The device according to at least one of the preceding claims 28 to 45, characterized by a bypass (71) in the flow path of the circulating air flow (UL) with controllable bypass flaps (71 1, 712) and a bypass line (713) for passing the circulating air flow (UL) the high-performance filter (61) and a bypass (72) in the outside air supply air flow path (AL / ZL) with controllable bypass flaps

(721, 722) and a bypass line (723) for bypassing the supply air flow (ZL) to the high-performance filter (59), wherein the bypass flaps (71 1, 712 or 721, 722) are independently controllable and by a control device in such a Position adjustable are that the air flows at low humidity either the high-performance filter (57, 61) or through the bypass lines

(713, 723) are guided past the high-performance filters 57, 61

47. The device according to at least one of the preceding claims 28 to 46, characterized by additional dehumidification heat pump systems in the outside air supply air (AL-ZL) and circulating air (UL), wherein in the flow path of the circulating air flow (UL) provided additional Entfeuchtungswärmepumpensystem before from the waste heat of electrical and electronic units (16) in the unit module (15) fed heating device (65) is arranged and from an evaporator / cooler (62), compressor (63), a first condenser (64) and an outdoor air in the outside air supply (AL -ZL) arranged second condenser / reheat register (66), which is associated with the first capacitor / reheat register (64) and with this common or mutually operable, while in the outside air supply air flow path (AL-ZL) arranged Dehumidification heat pump system from an evaporator / cooler (53), compressor (54), a first capacitor / reheat register (55) and / or a second condensate ator / reheat register (59) with reciprocal mode of operation.

48. The device according to at least one of the preceding claims 29 to 47, characterized in that a jet nozzle (80) for blowing a Zuluftstromes in the entrance of the tower (10) is arranged at high speed in the center of the tower diameter.

49. The device according to at least one of the preceding claims 29 to 48, characterized by on intermediate decks of the tower (10) arranged mechanical air conveyors, in particular fans (80, 81, 82), for increasing the dynamic velocity of the supply air stream (ZL, ZL ', ZL ", ZL '").

50. Apparatus according to claim 49, characterized in that the mechanical air conveying devices (80, 81, 82) with preferably from the waste heat in the unit module (15) arranged in the heat-dissipating electrical and electronic units (16) fed heaters (8, 83, 84) are connected.

51. The device according to at least one of the preceding claims 28 to 50, characterized in that in parts or areas of the tower (10) or the nacelle (1 1) of the wind energy plant (1) with additional cooling demand an air treatment device (94) with recuperative Heat recovery system and hermetically separated from each other first and second flow paths is arranged, wherein the first flow path outside air (AL) leads to the exhaust air (FL) and the second flow path in recirculation mode intake air (ZL, ZL ') sucks and indirectly as freely cooled down supply air (ZL ").

52. Apparatus according to claim 51, characterized in that in the flow path of the indirectly freely cooled supply air (ZL "), a mechanical cooling device (970 to 972) is arranged.

53. Device according to at least one of the preceding claims 28 to 52, characterized in that at least one speed increasing device, preferably a fan and a nozzle, in the tower (10) is arranged, the air at high speed obliquely upward, upwards on the tower wall and generates a rotary movement or vortex flow in the tower (10).

54. Apparatus according to claim 53, characterized in that the nozzle has a round shape or a flat-jet shape.