kinematic analysis of a flapping-wing micro-aerial-vehicle with watt
TRANSCRIPT
Kinematic Analysis of a Flapping-wing
Micro-aerial-vehicle with Watt Straight-line Linkage
Chao-Hwa Liu* and Chien-Kai Chen
Department of Mechanical and Electro-mechanical Engineering, Tamkang University,
Tamsui, Taiwan 251, R.O.C.
Abstract
In this study kinematic analysis of a particular flapping wing MAV is performed to check the
symmetry of the two lapping wings. In this MAV symmetry is generated by a Watt straight line
mechanism. After appended by two more links to provide a continuous input, and it becomes a
Stephenson type III six-bar linkage. Together with the two wings the vehicle has 10 links and 13 joints.
Since a Watt four-bar linkage can only generate approximate straight lines, the deviation from an exact
straight line causes phase lags of the two wings. The goal of this study is to determine the phase lags.
To achieve this goal a forward kinematic analysis of the Stephenson III linkage is performed, which
refers to the procedures that may determine the position, velocity, and acceleration of the MAV.
Among these procedures, position analysis involves equations that are highly nonlinear and deserves
special attention.
The authors developed two solution techniques for the forward position analysis of Stephenson
III mechanisms: an analytic procedure which leads to closed-from solutions; and a numerical
technique to obtain approximate solutions. We use the numerical technique to perform kinematic
analysis because solutions obtained by the two methods agree almost exactly but the numerical method
is much faster. We analyzed the MAV with the same dimension as the real model, and found it to have
very good symmetry with negligible phase lags between the two wings.
Key Words: Micro-aerial-vehicle, Forward Position Analysis, Watt Straight-line Linkage, Stephenson
Type III six-bar Linkage
1. Introduction
Recently many research efforts have been made on
design and construction of Micro Aerial Vehicles (MAV).
Insect-like MAVs generally have two flapping wings, and
various mechanisms to drive the wings have been sug-
gested and tested. For example, Yang [1] utilized a four-
bar crank-rocker linkage in his flapping wing device.
Galinski and Zbikowski [2] developed a mechanism in
which a double rocker linkage is driven by a crank rocker
mechanism. Galinski and Zbikowski [3] made use of a
double spherical Scotch yoke mechanism to generate de-
sired motion. The mechanism developed by McIntosh et
al. [4] includes planar four-bar linkages, spatial cam me-
chanisms, and slotted arms. Zhang et al. [5] used a mech-
anism with a spatial single crank double rocker mecha-
nism. Yang, et al. [6] demonstrated the design, fabrica-
tion, and performance test of a 20 cm-span MAV, which
has a flapping angle up to 100�. Recently, a model of a
flapping wing MAV is proposed [7], the basic structure
of which consists of a Stephenson type III six-bar mecha-
nism that includes a Watt four-bar linkage, and two wing
mechanisms. Symmetry of the two wings is due to the
straight line motion generated by the Watt four-bar link-
Journal of Applied Science and Engineering, Vol. 18, No. 4, pp. 355�362 (2015) DOI: 10.6180/jase.2015.18.4.06
*Corresponding author. E-mail: [email protected]
This paper is the extension from the authors’ technical abstract pre-
sented in the 1st International Conference on Biomimetics And Orni-
thopters (ICBAO-2015), held by Tamkang University, Tamsui, Taiwan,
during June 28�30, 2015.
age. However, a Watt four bar linkage can only generate
an approximate straight-line, the purpose of this study,
therefore, is to determine the difference, or the phase lag,
between the two wings. Phase lags include differences of
the two wings in position, velocity, and acceleration. Ki-
nematic analysis must be performed to determine posi-
tion, velocity, and acceleration of the mechanism.
The paper is organized as follows. The construction
of the mechanism is introduced in the next section; then
the procedure for position analysis is discussed in sec-
tion 3. Velocity and acceleration analysis procedures are
explained in section 4. Analysis results are shown in
section 5, followed by the conclusion in section 6.
2. Construction of the Mechanism
Figure 1 is an illustrative diagram for the flapping
wing MAV proposed by Cheng [7]. The mechanism has
10 links and 13 pin joints. Links�,�,�, and� con-
stitute a Watt four-bar mechanism that makes joint C
moving along an approximate straight line. A Stephen-
son type III six-bar linkage is formed by adding links�
and� to the Watt straight line mechanism. The reason
for adding these two links is obvious, since not a single
link in the Watt mechanism is able to make a full revolu-
tion. With two links added, input to this mechanism is
the continuous rotation of link � generated by a motor.
Finally, links� and links� are the right wing and
the left wing mechanisms, and flapping of both wings
are produced by motion of joint C. Symmetric motion of
the two wings is achieved if joint C moves along a perfect
straight line along the vertical direction, which can only
be generated by more complex mechanisms [8]. In the
current design, the Watt four-bar linkage is used to reduce
number of links and total weight, the cost of using this
simple linkage is that this mechanism can only produce
approximate straight lines. In the subsequent analysis,
we determine the phase lag of the two links when link�
rotates with a constant angular velocity.
3. Position Analysis
3.1 Stephenson Type III Six-bar Linkage
Position analysis of the Stephenson type III six-bar
linkage is performed first, from which the position of joint
C in Figure 1, as a function of position of the input link,
may be determined. Previous study includes Jawad [9]
who obtained algebraic equations that govern the posi-
tion of this linkage, and he solved the equations numeri-
cally. Watanabe and Funabashe [10,11] obtained solu-
tions for positions of various Stephenson six-bar linkages
by solving six order algebraic equations. Watanabe et al.
[12] extended this study to 23 planar linkages with a si-
milar construction. Since these solution techniques in-
volve equations with page-long coefficients, in this study
we developed different methods to obtain solutions, as
introduced below.
Figure 2 shows a general Stephenson type III six-bar
linkage driven by link�. When dimension of all links
are known, the purpose is to determine position vari-
ables �3, �4, �5, and �6, for a given input angle �2. The
Stephenson III linkage is composed of a four-bar linkage
that includes links ��, and a two-bar chain that
contains links��. Note that the separation of this six-
bar linkage this way has been suggested by Watanabe and
356 Chao-Hwa Liu and Chien-Kai Chen
Figure 2. A Stephenson type III six-bar linkage.Figure 1. An illustrative diagram for a flapping wing MAV.
Funabashe [10,11]. Yet they used this idea in determin-
ing limiting positions of the linkage, not in determining
positions in general. In the following, we will discuss
two techniques based upon this separation, one leads to
closed-form solutions and the other is numerical in na-
ture.
In the first method, the point D in Figure 2 is con-
sidered as the intersection of two curves. The first curve
is the circle of radius L3, whose center G may be deter-
mined from input angle �2. The second curve, called cou-
pler curve, is the curve generated by D as the four-bar link-
age �� is in motion. Figure 3 illustrates a portion
of the coupler curve for an arbitrary four-bar linkage. Us-
ing the notations used in Figure 3, the coupler curve is a
sixth degree polynomial whose equation is [13].
(1)
Closed-form solutions for position analysis of a Stephen-
son III six-bar linkage are obtained by locating intersec-
tions of the two curves, and they are found by MATLAB
in this study. Each real solution so obtained is a position
of the joint D in Figure 2. As long as the location of D is
known, �3, �4, �5, and �6 may be calculated by geometric
relations.
In the second method, we choose link (or link)
as the driving link to the four-bar linkage BCDEF in Fig-
ure 2. For each given value of �5, values of �4, �6, and the
corresponding positions of the point D may be calcu-
lated using analytical expressions that may be found in
a textbook such as [8]. Then, for this particular value of
�5, the distance between D and the known position of G
is calculated. The purpose now is to determine the va-
lues of �5 so that the distance DG equals to L3. The pro-
cedure used in this study to determine these values is as
follows. We first incrementally search for intervals of �5
within which the value (DG � L3) changes sign, then the
bisection method is used in these intervals to locate va-
lues of �5 which make (DG � L3) nearly zero.
As a check of these two procedures, we analyzed the
Stephenson III six-bar linkage in Figure 2 with the non-
dimensioned lengths: a = 5, b = 13, c = 8, d = 4, e = 6.5, f
= 3, L2 = 1, L3 = 6, L5 = 1, L6 = 3, and input angle �2 =
300�, Convergence criterion for numerical procedure is
that convergence is achieved when �DG � L3� < 10-10.
Two solutions are found for this problem and they are
given in Table 1. One may observe that results obtained
from the two procedures agree up to at least 7 digits after
the decimal point. Since the numerical procedure is fas-
ter, the following results for position analysis are calcu-
lated by this procedure.
3.2 Wing Mechanisms
Figure 4 shows the Stephenson III six-bar linkage in
the flapping wing MAV. As a value of input angle �2 is
given, positions of all other links may be found by the
method just been discussed, and from these positions the
coordinates of C, namely Cx and Cy, can be calculated.
When the position of C is found, joint D of the right wing
mechanism (Figure 1) can be located since it is the inter-
section of the following two circles, the circle centers at
Kinematic Analysis of a Flapping-wing Micro-aerial-vehicle with Watt Straight-line Linkage 357
Table 1. Comparison of results obtained using two
procedures; differences are underlined
Closed-form Numerical
1st sol �21.0981401119277� �21.0981401120935��3 2nd sol �9.34660961319297� �9.34660961312838�
1st sol 28.1602559557637� 28.1602559560016��4 2nd sol 22.7638442767922� 22.7638442768305�
1st sol 189.74678710913� 189.74678711034��5 2nd sol 113.48012093066� 113.48012092989�
1st sol 145.052820929300� 145.052820929443��6 2nd sol 124.750245471184� 124.750245470924�Figure 3. A part of the coupler curve generated by the point D
on the coupler of a four-bar linkage.
C with a radius L4, and the circle centers at E whose ra-
dius is L5. In general, there are two intersections, as
shown in Figures 5 and 6. The first solution shown in
Figure 5 is given by
(2)
where R is the known distance between C and E, and
(3)
The second solution as shown in Figure 6 contains the
following two angles
(4)
(5)
Note that, generally the two solutions do not intersect.
Once the right wing is assembled in either of the two
ways, it remains the same configuration unless it is dis-
connected and reassembled.
The left wing also has two solutions, given by [13]
(6)
(7)
and
(8)
(9)
4. Velocity and Acceleration Analysis
Velocity analysis is performed after the position analy-
sis, that is, when all link positions have been found. The
order for velocity analysis is similar to that for position
analysis; the Stephenson III six-bar linkage must be treated
first, since both wings are driven by it.
4.1 Stephenson Type III Six-bar Linkage
The Stephenson III linkage illustrated by Figure 4
has the following two closed loops:
358 C. H. Liu and Chien-Kai Chen
Figure 4. The Stephenson III six-bar linkage in the MAV.
Figure 5. The first solution for the position analysis of theright wing mechanism.
Figure 6. The second solution for the position analysis of theright wing mechanism.
AB + BC + CG = AI + IG (10)
HF + FG = HI + IG (11)
The x and y components of equation (10) are
(12)
(13)
Similarly vector equation (11) has the following two
components
(14)
(15)
Differentiating these four equations once with respect
to time, one may obtain
(16)
where the matrix M1 is given by
(17)
With positions of all links known, for a given input ve-
locity �� 2 one may solve equation (16) for unknown ve-
locities �� 3, �� 8 , �� 9 and �� 10.
4.2 Wing Mechanisms
Referring to Figure 7, one may notice the vector loop
closure equation for the right wing
AB + BC + CD = AE + ED (18)
The x and y components of this equation are
(19)
(20)
Upon differentiation, we may obtain
(21)
where
(22a)
(22b)
Angular velocities �� 4 and �� 5 may be found from equa-
tion (21). Finally, the loop equations for the left wing is
(see Figure 8)
AB + BC + CK = AJ + JK (23)
Following the same procedure as before, one may ob-
tain [13]
(24)
in which
(25)
Kinematic Analysis of a Flapping-wing Micro-aerial-vehicle with Watt Straight-line Linkage 359
Figure 7. Notations of the right wing mechanism for velocityand acceleration analysis.
From these equations the velocities ��6 and �� 7 can be ob-
tained.
Unknown accelerations may be calculated when posi-
tions, velocities, and driving accelerations ��� 2 are known.
Equations for calculating accelerations are obtained by
differentiating velocity equations (16), (21), and (24).
For the Stephenson III six-bar linkage, the equation is
(26)
where
(27)
After accelerations ��� 3, ��� 8 , ��� 9 , and ��� 10 are obtained from
equation (26), accelerations for the right wing and the
left wing may be found from
(28)
and
(29)
5. Results and Discussions
The dimension for the MAV, as illustrated by Figure
1, is as follows [7]: AB = L2 = 2 mm, BC = L3 = 16 mm,
CD = L4 = 6.5 mm, CK = L6 = 6.5 mm, DE = L5 = 3 mm,
JK = L7 = 3 mm, GI = L8 = 10 mm, HF = L9 = 10 mm, GF
= L10 = 4 mm, and GC = FC = 2 mm. These lengths are
used in the subsequent analysis. Figure 9 shows the par-
ticular configuration obtained from position analysis
when �2 = 0. Angular position �5 of the right wing is
shown in Figure 10. Note that the angle �5 defined in
Figure 7 is not the flapping angle. The flapping angle
generally refers to the angle by which the wing extends
outward from the body (see Figure 1). The two angles al-
ways differ by a constant. The angular stroke of the wing,
also called flapping range, is the maximum difference in
�5. For this mechanism its value is 70.6�. To check the
symmetry between the two wings, we compare the angle
�� 5 in Figure 7, to the angle �7 in Figure 8; also we com-
pare and the angle �4 in Figure 7 to the angle ��6 in Fig-
ure 8. The differences between these angles are shown
in Figure 11. The maximum difference in this figure is
between �� 5 and �7, its value is 0.0825�, and it occurs
when �2 = 90�. The coupler curve generated by the point
360 Chao-Hwa Liu and Chien-Kai Chen
Figure 9. Configuration of the flapping wing MAV when �2
= 0.Figure 8. Notations of the left wing mechanism for velocity
and acceleration analysis.
C on the Watt linkage approximates a vertical straight
line. The position �2 = 90� corresponds to one extreme
position for joint C where it begins to deviate further
from a straight line, causing a larger degree of asym-
metry of the two wings at this position.
Results for velocity and acceleration analysis are
obtained with the constant input velocity �2 = 1 rad/s.
The difference in angular velocity between link � and
link is shown in Figure 12. The maximum value in
this figure is 8.8048 � 10-5 rad/s and it occurs when �2 =
113�. In Figure 13 we show the velocity difference be-
tween link and link�. Its maximum value is 4.8085
� 10-5 rad/s, which occurs when �2 = 114�. The differ-
ence in acceleration between link� and link is shown
in Figure 14. The maximum difference is 3.583525 �
10-4 rad/s2, which occurs at the position �2 = 90�. Finally,
the difference in acceleration between link and link�
is shown in Figure 15. The maximum difference occurs
when �2 = 100�, whose value is 1.820966 � 10-4 rad/s2.
6. Conclusions
In this study we show that a Stephenson III six-bar
Kinematic Analysis of a Flapping-wing Micro-aerial-vehicle with Watt Straight-line Linkage 361
Figure 11. Phase lag of the two wings.
Figure 12. Velocity difference between link� and.
Figure 13. Velocity difference between link and link�.
Figure 14. Acceleration difference between link� and link.
Figure 10. Angular position of link.
linkage may be viewed as two separate mechanisms in
forward position analysis. Based on this separation, two
techniques for position analysis of this linkage are sug-
gested. While one technique may lead to closed-form so-
lution without any iterative procedure, the numerical te-
chnique is much faster and converges to nearly the same
value obtained by using closed-form solution. The nu-
merical technique is used for position analysis of a flap-
ping wing MAV whose basic structure is Stephenson III
six-bar linkage. We find the two wings of this MAV are
highly symmetric and phase lags of the two wings are in-
significant.
Acknowledgements
The authors gratefully acknowledge that this study
was supported by the National Science Council of ROC
under Grant NSC 101-2632-E-032-001-MY3.
References
[1] Yang, L. J., U.S. Patent 8,033,499B2 (2011).
[2] Galinski, C. and Zbikowski, R., “Materials Challenges
in the Design of an Insect-like Flapping Wing Mecha-
nism Based on a Four-bar Linkage,” Materials and
Design, Vol. 28, pp. 783�796 (2007). doi: 10.1016/j.
matdes.2005.11.019
[3] Galinski, C. and Zbikowski, R., “Insect-like Flapping
Wing Mechanism Based on a Double Spherical Scotch
Yoke,” Journal of the Royal Society Interface, Vol. 2,
No. 3, pp. 223�235 (2005). doi: 10.1098/rsif.2005.
0031
[4] McIntosh, S., Agrawal, S. and Khan, Z., “Design of a
Mechanism for Biaxial Rotation of a Wing for a Hover-
ing Vehicle,” IEEE/ASME Transactions on Mecha-
tronics, Vol. 11, No. 2, pp 145�153 (2006). doi: 10.
1109/TMECH.2006.871089
[5] Zhang, T., Zhou, C., Zhang, X. and Wang, C., “Design,
Analysis, Optimization and Fabrication of a Flapping
Wing MAV,” Proceedings of 2011 International Con-
ference on Mechatronic Science, Electric Engineering
and Computer, Jilin, China, pp. 2241�2244 (2011). doi:
10.1109/MEC.2011.6025938
[6] Yang, L. J., Esakki, B., Chandrasekhar, U., Huang,
K.-C. and Cheng, C.-M., “Practical Flapping Mecha-
nisms for 20 cm-Span Micro Air Vehicles,” Interna-
tional Journal of Micro Air Vehicles, Vol. 7, No. 2, pp.
181�202 (2015). doi: 10.1260/1756-8293.7.2.181
[7] Cheng, C.-M., Preliminary Study of Hummingbird-
like Hover Mechanisms, Master Thesis, Tamkang Uni-
versity, Damsui Dist., New Taipei, City, Taiwan (2013).
[8] Norton, R. L., Design of Machinery: an Introduction to
the Synthesis and Analysis of Mechanisms and Ma-
chines, 5’th ed., McGraw-Hill, New York (2012).
[9] Jawad, S. N. M., “Displacement Analysis of Planar
Stephenson Mechanism,” Proceedings of the Interna-
tional Computers in Engineering Conference, Vol. 2,
pp. 664�669 (1984).
[10] Watanabe, K. and Funabashi, H., “Kinematic Analysis
of Stephenson Six-link Mechanisms,” (1st Report),
Bulletin of the JSME, Vol. 27, No. 234, pp. 2863�2870
(1984). doi: 10.1299/jsme1958.27.2863
[11] Watanabe, K. and Funabashi, H., “Kinematic Analysis
of Stephenson Six-link Mechanisms,” (2nd Report),
Bulletin of the JSME, Vol. 27, No. 234, pp. 2871�2878
(1984). doi: 10.1299/jsme1958.27.2871
[12] Watanabe, K., Zong, Y. H. and Kawai, Y., “Displace-
ment Analysis of Complex Six Link Mechanisms of
the Stephenson-type,” JSME International Journal,
Vol. 30, No. 261, pp. 507�514 (1987). doi: 10.1299/
jsme1987.30.507
[13] Chen, C.-K., Kinematic and Error Analysis of a Hum-
mingbird-like Micro-aerial-vehicle, Master Thesis,
Tamkang University, Damsui Dist., New Taipei, City,
Taiwan (2014).
Manuscript Received: Sep. 9, 2015
Accepted: Oct. 23, 2015
362 Chao-Hwa Liu and Chien-Kai Chen
Figure 15. Acceleration difference between link and link�.