Michael Graham - Wind Energy Handbook

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Discover this fully updated and authoritative reference to wind energy technology written by leading academic and industry professionals  The newly revised Third Edition of the 
 delivers a fully updated treatment of key developments in wind technology since the publication of the book’s Second Edition in 2011. The criticality of wakes within wind farms is addressed by the addition of an entirely new chapter on wake effects, including ‘engineering’ wake models and wake control. Offshore, attention is focused for the first time on the design of floating support structures, and the new ‘PISA’ method for monopile geotechnical design is introduced. 
The coverage of blade design has been completely rewritten, with an expanded description of laminate fatigue properties and new sections on manufacturing methods, blade testing, leading-edge erosion and bend-twist coupling. These are complemented by new sections on blade add-ons and noise in the aerodynamics chapters, which now also include a description of the Leishman-Beddoes dynamic stall model and an extended introduction to Computational Fluid Dynamics analysis. 
The importance of the environmental impact of wind farms both on- and offshore is recognised by extended coverage, which encompasses the requirements of the Grid Codes to ensure wind energy plays its full role in the power system. The conceptual design chapter has been extended to include a number of novel concepts, including low induction rotors, multiple rotor structures, superconducting generators and magnetic gearboxes.
References and further reading resources are included throughout the book and have been updated to cover the latest literature. Importantly, the core subjects constituting the essential background to wind turbine and wind farm design are covered, as in previous editions. These include: 
The nature of the wind resource, including geographical variation, synoptic and diurnal variations and turbulence characteristics The aerodynamics of horizontal axis wind turbines, including the actuator disc concept, rotor disc theory, the vortex cylinder model of the actuator disc and the Blade-Element/Momentum theory Design loads for horizontal axis wind turbines, including the prescriptions of international standards Alternative machine architectures The design of key components Wind turbine controller design for fixed and variable speed machines The integration of wind farms into the electrical power system Wind farm design, siting constraints and the assessment of environmental impact Perfect for engineers and scientists learning about wind turbine technology, the 
 will also earn a place in the libraries of graduate students taking courses on wind turbines and wind energy, as well as industry professionals whose work requires a deep understanding of wind energy technology.

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(3.1) The symbol refers to conditions far upstream D refers to conditions at the - фото 122

The symbol ∞ refers to conditions far upstream, D refers to conditions at the disc, and W refers to conditions in the far wake.

It is usual to consider that the actuator disc induces a velocity variation that must be superimposed on the free‐stream velocity. The streamwise component of this induced flow at the disc is given by − aU ∞, where a is called the axial flow induction factor , or the inflow factor . At the disc, therefore, the net streamwise velocity is

(3.2) Wind Energy Handbook - изображение 123

Figure 32 An energy extracting actuator disc and streamtube 321 Simple - фото 124

Figure 3.2 An energy extracting actuator disc and streamtube.

3.2.1 Simple momentum theory

The air that passes through the disc undergoes an overall change in velocity, U ∞− U W, and a rate of change of momentum equal to the overall change of velocity times the mass flow rate:

(3.3) The force causing this change in momentum comes entirely from the pressure - фото 125

The force causing this change in momentum comes entirely from the pressure difference across the actuator disc and the axial component of the pressure acting on the curved surface of the streamtube. This latter pressure is usually assumed to be ambient and therefore to give zero contribution, without further explanation. In fact this pressure is different from ambient due to the axial variation of velocity along the streamtube, but the integral of its axial component from far upstream to far downstream can be shown to be exactly equal to zero, the streamwise contribution upstream of the actuator disc exactly balancing the downstream contribution that opposes the stream (Jamieson 2018).

Therefore,

(3.4) To obtain the pressure difference p D p D Bernoullis equation is - фото 126

To obtain the pressure difference ( p D +− p D −), Bernoulli's equation is applied separately to the upstream and downstream sections of the streamtube: separate equations are necessary because the total energy is different upstream and downstream. Bernoulli's equation states that, under steady conditions, the total energy in the flow, comprising kinetic energy, static pressure energy, and gravitational potential energy, remains constant provided no work is done on or by the fluid. Thus, for a unit volume of air,

(3.5a) Upstream therefore we have 35b Assuming the flow speed to be at low Mach - фото 127

Upstream, therefore, we have

(3.5b) Assuming the flow speed to be at low Mach number M typically M 03 is - фото 128

Assuming the flow speed to be at low Mach number M (typically M < 0.3 is sufficient), it may be treated as incompressible ( ρ ∞= ρ D) and to be independent of buoyancy effects ( ρgh ∞= ρgh D) then,

(3.5c) Similarly downstream 35d Subtracting these equations we obtain 36 - фото 129

Similarly, downstream,

(3.5d) Subtracting these equations we obtain 36 Equation 34then gives 37 - фото 130

Subtracting these equations, we obtain

(3.6) Wind Energy Handbook - изображение 131

Equation (3.4)then gives

(3.7) Wind Energy Handbook - изображение 132

and so,

(3.8) Wind Energy Handbook - изображение 133

That is, half the axial speed loss in the streamtube takes place upstream of the actuator disc and half downstream.

3.2.2 Power coefficient

The force on the air becomes, from Eq. (3.4),

(3.9) As this force is concentrated at the actuator disc the rate of work done by - фото 134

As this force is concentrated at the actuator disc, the rate of work done by the force is TU Dand hence the power extraction from the air is given by

(3.10) A power coefficient is then defined as 311 where the denominator - фото 135

A power coefficient is then defined as

(3.11) Wind Energy Handbook - изображение 136

where the denominator represents the power available in the air, in the absence of the actuator disc.Therefore,

(3.12) Wind Energy Handbook - изображение 137

3.2.3 The Betz limit

(This limit is also referred to as the Lanchester–Betz limit or the Betz–Joukowski limit ). 1

The maximum value of C Poccurs when

that gives a value of Hence 313 The maximum - фото 138

that gives a value of Hence 313 The maximum achievable value of the power coefficient is known - фото 139

Hence,

(3.13) The maximum achievable value of the power coefficient is known as the Betz - фото 140

The maximum achievable value of the power coefficient is known as the Betz limit after Albert Betz (1919), the German aerodynamicist. Frederic Lanchester (1915), a British aeronautical pioneer, worked earlier on a similar analysis and is sometimes given prior credit, and Joukowski (1920) also contributed an analysis. To date, no unducted wind turbine has been designed that is capable of exceeding the Betz limit. The limit is caused not by any deficiency in design because, as yet in our discussion, we have no design. However, because the streamtube has to expand upstream of the actuator disc, the cross‐section of the tube where the air is at the full, free‐stream velocity is smaller than the area of the disc.

The efficiency of the rotor might more properly be defined as

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