Environmental Engineering Reference
In-Depth Information
Fig. 6.9 Three-mass drive
train model of a wind system
T wind turbine; B gear box;
G generator
R 4
L
J = 2 π
K = G
R 4 L
;
2 π
(6.50)
Note that the inertia values of two disks in series are added, J = J 1 + J 2 , while
the spring constant of two cylindrical shaft elements in series follows 1 / K = 1 / K 1 +
1 / K 2 . The differential equation assigned to Fig. 6.9 becomes:
+
+
=
J T
ϕ T
ϕ B
ϕ G
D T
ϕ T
ϕ B
ϕ G
K TB K TB
K TB ( K TB + K BG ) K BG
K BG
ϕ T
ϕ B
ϕ G
T T
J B
D B
J G
D G
K BG
T G
In this model damping effects in the steel shafts and in couplings are neglected,
and only viscous damping losses are considered. When a gear-box is present, all
quantities have to be referred to either the low-speed side or the high-speed side.
Normally it is the latter, i.e. the generator side. The parameters of the turbine side
must be referred to the generator side using the speed ratio; as example the equiva-
lent turbine inertia is calculated as:
J T = ω G
ω
2
J T
T
A parameter example of realistic wind energy systems shows that the relation
J T : J B : J G is in the region of 12:0, 6:1. In conclusion a two-mass system may be
used as reduced order model. Then the gear box inertia J B is mostly halved, with the
halves added to either side, on the other hand simulation results recommend adding
the total gear-box value to the generator.
The two-mass model improves considerably the one-mass representation; it al-
lows for determining one mechanical eigenfrequency and estimation of transient
torques stressing shafts and couplings. Therefore its properties are discussed shortly.
Defining the difference
ϕ
G as the torsion angle, a second order linear
differential equation can be established:
ϕ
=
ϕ
T
+ D 1
J T
+ K 1
J T
1
J G
1
J G
= T T
J T
+ T G
J G
ϕ
¨
+
ϕ
˙
+
ϕ
(6.51)
2 dv 0
0
ν
The two-mass system features a damping coefficient d and a characteristic fre-
quency
ν 0 . Since damping values of the shaft train are low, the response to a step
 
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