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**Research article**
12 Jun 2019

**Research article** | 12 Jun 2019

Stability analysis of bicycles

^{1}Department of Industrial Engineering, University of Padova, Padova, 35131, Italy^{2}Department of Mechanical Engineering, Universidad de los Andes, Bogota, 111711, Colombia

^{1}Department of Industrial Engineering, University of Padova, Padova, 35131, Italy^{2}Department of Mechanical Engineering, Universidad de los Andes, Bogota, 111711, Colombia

Abstract

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The basic Whipple-Carvallo bicycle model for the study of stability takes into account only geometric and mass properties. Analytical bicycle models of increasing complexity are now available, they consider frame compliance, tire properties, and rider posture. From the point of view of the designer, it is important to know if geometric and mass properties affect the stability of an actual bicycle as they affect the stability of a simple bicycle model. This paper addresses this problem in a numeric way by evaluating stability indices from the real parts of the eigenvalues of the bicycle's modes (i.e., weave, capsize, wobble) in a range of forward speeds typical of city bicycles. The sensitivity indices and correlation coefficients between the main geometric and mass properties of the bicycle and the stability indices are calculated by means of bicycle models of increasing complexity. Results show that the simpler models correctly predict the effect of most of geometric and mass properties on the stability of the single modes of the bicycle. Nevertheless, when the global stability indices of the bicycle are considered, often the simpler models fail their prediction. This phenomenon takes place because with the basic model some design parameters have opposite effects on the stability of weave and capsize, but, when tire sliding is included, the capsize mode is always stable and low speed stability is chiefly determined by weave stability.

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Doria, A., Roa, S., and Muñoz, L.: Stability analysis of bicycles by means of analytical models with increasing complexity, Mech. Sci., 10, 229-241, https://doi.org/10.5194/ms-10-229-2019, 2019.

1 Introduction

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The stability of bicycles has drawn the attention of scientists since the development of the first modern bicycles. The first dynamic models for understanding the bicycle dynamics were written independently by two scientists at the end of the nineteenth century: Whipple (1899) and Carvallo (1899). The Whipple–Carvallo bicycle model (WCBM) (Meijaard et al., 2007) consists in the linearized equations of motion of the bicycle and the rider. This model makes it possible to conduct open loop analysis with the rider hands-off the handlebar. Many authors have analyzed bicycle stability using the WCBM (Limebeer and Sharp, 2006; Meijaard et al., 2007; Schwab et al., 2007; Sharp, 2008) by solving the eigenvalue problem in order to analyze the modes of vibration of the system.

Starting from the WCBM many linearized bicycle models of increasing complexity have been developed to study bicycle stability. Some researchers have extended the WCBM in order to include compliance of the front assembly (CFA). This compliance commonly includes the effects of the frame head tube, the fork, and the wheel (Doria and Roa, 2017; Doria et al., 2017; Klinger et al., 2014; Limebeer and Sharp, 2006; Plöchl et al., 2012; Sharp, 2008). These models add an additional velocity degree of freedom to the WCBM in order to take into account the lateral velocity of the front-assembly due to compliance. Other authors have extended the model including tire mechanics (Doria et al., 2013; Doria and Roa, 2017; Klinger et al., 2014; Sharp, 2008; Souh, 2015). When tire lateral slip is considered at least four degrees of freedom (DOFs) are needed to model the bicycle.

Even if bicycle tires may exhibit a non-linear behavior (Doria et al., 2013) and the shock absorbers that nowadays equip many bicycles have non-linear characteristics (Cossalter et al., 2010), very few authors have carried out stability analysis taking into account non-linear properties (Bulsink et al., 2015), because stability analysis with non-linear models requires cumbersome time-domain simulations and specific identification methods for extracting the properties of the modes of vibration from time-domain data.

The rider with his/her mass, stiffness and damping characteristics has a large effect on bicycle dynamics, even if the control actions (Kooijman and Schwab, 2013) are neglected and a completely passive behavior is assumed. For this reason, some researchers have integrated the bicycle model with rider models composed of rigid bodies (the limbs) connected by means of joints (the articulations) and by lumped stiffness and damping elements (Schwab et al., 2012; Doria and Tognazzo, 2014). These models make it possible to simulate the passive response of the rider both in the hands-off and in the hands-on configuration.

The extensions of the WCBM improve the quality and range of reliability of the stability analysis. For instance, when the front-assembly compliance and tire mechanics are included, the wobble mode appears as an additional mode of vibration and bicycle stability at relatively high speed is better predicted. Additionally, when the hands-on condition is analyzed, the weave, capsize and wobble modes are changed with respect to the hands-off condition, in particular the wobble mode becomes more damped due to the rider's arms influence (Klinger et al., 2014; Roa et al., 2018). Nonetheless, it is useful to determine the limits and potentialities of each model.

The purpose of this paper is to compare different models of increasing complexity in terms of their capability of predicting bicycle stability. Since bicycle stability depends on many parameters, only the effect of geometrical properties is analysed, tire properties, stiffness properties, and rider body properties are kept constant. The possible geometric configurations are explored numerically with a design of experiment (DOE) approach based on the space filling method proposed by Sobol (1967). This method compared with a random method assures a lower uncertainty for the same number of sample points (Saltelli et al., 2008) which are associated with the computational effort. The stability of each bicycle configuration is evaluated by means of numerical indices that are calculated from the eigenvalues obtained by means of the models of increasing complexity.

2 Bicycle models

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The simplest model considered in this research is the WCBM, that was checked
and reviewed in Meijaard et al. (2007). This model has two velocity degrees
of freedom (DOFs): the steer rotation of the handlebar around the steering
axis $\dot{\mathit{\delta}}$, and the roll rotation of the rear frame and rider
around the longitudinal axis $\dot{\mathit{\phi}}$. Since the bicycle components
(front frame, rear frame, and wheels) and the rider are assumed to be rigid
bodies and the wheels are assumed to be rigid disks, which roll without
sliding, the stability features foreseen by this model depend only on the
geometric and mass properties. A set of 25 geometric and mass properties is
needed to describe this bicycle model (Meijaard et al., 2007). Actually,
some of these parameters cannot be affected by the designer, e.g. rear
assembly (rear frame plus rider) mass and inertia chiefly depend on the
properties of the rider's body. Other parameters are interconnected, e.g.
wheel mass and inertia depend on the radius of the wheel. For this reason, a
reduced set of parameters is considered in this research, they are: the
front and rear wheel radii (*r*_{F} and *r*_{R}), mass *m*_{H} of fork plus handlebar, wheelbase (*w*), trail (*c*), caster angle (*λ*), and the
coordinates of the center of mass of the rear assembly (*x*_{B} and
*z*_{B}), which largely depend on the position of the saddle. Since the aim
of this research is the study of the single effect of each of these eight
parameters, the mathematical model was carefully implemented in order to
avoid that the variation in a parameter affects other parameters. Figure 1a
shows the WCBM with the design parameters.

The second model considered in this research is the improvement of the WCBM recently proposed in Doria et al. (2017), see Fig. 1b. This model accounts for front assembly compliance by introducing a revolute joint, a rotational spring, and a rotational damper (not shown in the figure); the revolute joint defines the deformation axis of the front frame that makes possible the lateral displacement of the front wheel. Therefore, the number of DOFs increases to three, and the new variable $\dot{\mathit{\beta}}$ is the velocity about the deformation axis of the front frame. The values of rotational stiffness and damping and the position of the deformation axis were identified by means of experimental tests and are kept constant in all the numeric calculations here reported, they are summarized in Table 1.

The most complex bicycle model considered in this research is the one developed in Klinger et al. (2014). In this model lateral slips of front and rear tires are allowed. A linear model of tire forces and torques is adopted, since they depend in a linear way on side-slip and camber angles. The DOFs are five: $\dot{\mathit{\delta}}$, $\dot{\mathit{\phi}}$, $\dot{\mathit{\beta}}$, yaw rate of the rear frame $\dot{\mathit{\psi}}$ and lateral velocity of the rear frame $\dot{y}$, see Fig. 1c. Mean values of tire properties from experimental tests (Doria et al., 2013; Dressel and Rahman, 2012) have been adopted and are kept constant in the numerical calculations here reported. In particular, the values of cornering stiffness, camber stiffness and overturning stiffness that are reported in Table 1 are the mean values of the characteristics of six different tires tested in two laboratories. The values of self-aligning stiffness and twisting stiffness are the mean values of the characteristics of three tested tires.

In all the previous models the rider with the hands-off the handlebar is simulated assuming the center of mass and inertia properties as in Meijaard et al. (2007). The model developed in Klinger et al. (2014) makes it possible to simulate bicycle dynamics considering the rider with the hands-on the handlebar as well. In order to avoid introducing new DOFs, the rider's body is connected to the handlebars by means of arms equipped with joints located at the shoulders, elbows and wrists, according to the approach suggested in Schwab et al. (2012). In the hands-on model, a bent-forward posture is assumed, and the center of mass and inertia properties are modified accordingly (Moore et al., 2009).

3 Stability indices

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Stability of bicycles and powered-two-wheeled vehicles usually is analyzed by plotting the real and imaginary parts of the eigenvalues against forward speed (Meijaard et al., 2007). This research focuses on the stability of city bicycles and the nominal geometric and mass properties of the reference bicycle are set equal to the ones of the benchmark bicycle defined in (Meijaard et al., 2007). Figures 2–5 represent the eigenvalue plots of the bicycle with the reference parameters of Tables 1 and 2 that are obtained carrying out stability analysis by means of the four models here considered.

In the field of bicycle dynamics very few stability indices have been
defined. With reference to stability analysis carried out by means of the
WCBM, which predicts only the weave and capsize modes, weave speed
*v*_{wea}, capsize speed *v*_{cap}, and self-stability range
Ssr_{2} are defined, see Fig. 2. Weave speed is the lowest speed at
which the weave mode becomes stable (negative real part of the eigenvalue),
whereas capsize speed is the lowest speed at which the capsize mode becomes
unstable. *v*_{wea} and *v*_{cap} are modal stability indices,
because they give information about the stability of a specific mode of
vibration, but they do not tell if the bicycle is globally stable or
unstable. The third stability index (Ssr_{2}) is the speed range on
which the uncontrolled bicycle is stable ${v}_{\mathrm{wea}}<v<{v}_{\text{cap}}$ and it
is a global stability index. These indices are very simple and clear, but
they have a limit, since they do not give information about the level of
stability/instability.

The analysis of the eigenvalues plots becomes more complex when more
detailed models able to predict the wobble mode are used to study stability.
In this case, it is possible to introduce another modal stability index,
which is the wobble speed (*v*_{wob}) and represents the lowest
speed at which the wobble mode becomes unstable, see Fig. 3. Global
stability can be analyzed using the three modes stability index
(Ssr_{3}), which is the range of speeds on which all the three modes
(weave, capsize and wobble) are stable. It is worth noticing that in some
cases Ssr_{3} is determined by the weave and capsize modes only, because
the wobble mode becomes unstable at speeds larger than *v*_{cap} (see Fig. 3). In other cases, Ssr_{3} is determined by the weave mode only,
because the capsize and wobble modes are always stable in the range of speed
that is analyzed (see Fig. 4). In some cases, as in Fig. 5, Ssr_{3} is
determined by the weave and wobble mode, because capsize is always stable.

In order to improve the stability analysis, the concept of stability area (Doria and Roa, 2017) is used in the framework of this research.

Dealing with single mode stability, the stability area index is the area formed by the curve of the real part of an eigenvalue and the speed axis when this real part is negative:

$$\begin{array}{}\text{(1)}& {A}_{\text{mode}}=\underset{\mathrm{0}}{\overset{{v}_{\text{max}}}{\int}}{\mathit{\delta}}_{\text{mode}}\left(v\right)\cdot \mathit{Re}\left({\mathit{\gamma}}_{\text{mode}}\left(v\right)\right)\cdot \text{d}v\end{array}$$

$$\begin{array}{}\text{(2)}& {\mathit{\delta}}_{\text{mode}}\left(v\right)=\left\{\begin{array}{ll}\mathrm{1}& \mathit{Re}\left({\mathit{\gamma}}_{\text{mode}}\left(v\right)\right)\le \mathrm{0}\\ \mathrm{0}& \mathit{Re}\left({\mathit{\gamma}}_{\text{mode}}\left(v\right)\right)>\mathrm{0}\end{array}\right.\end{array}$$

In Eq. (1) *v* is speed, *v*_{max} the maximum speed considered in the
analysis, *γ*_{mode} the eigenvalue of a specific mode of vibration
(mode = weave, capsize, wobble) and *δ* is the index defined in Eq. (2). *A*_{mode} index quantify
the damping of a mode when it is stable, the larger the area, the larger the
damping. For this study, the value of *v*_{max} is chosen as 10 m s^{−1},
which defines the relevant range to city bicycles, which seldom reach larger
speeds. Racing bicycles and certain electrical bicycles can operate at
higher speed regimes. Some preliminary tests showed that, if the speed range
is increased, sometimes the eigenvalue plots are not simply the
extrapolations of those presented in this paper, therefore specific analyses
are required.

Global stability can be studied considering the self-stability area, which is the intersection of the stability areas of the modes. If two modes are considered:

$$\begin{array}{}\text{(3)}& {\text{SsA}}_{\mathrm{2}}={A}_{\text{wea}}\cap {A}_{\text{cap}}\end{array}$$

If three modes are considered:

$$\begin{array}{}\text{(4)}& {\text{SsA}}_{\mathrm{3}}={A}_{\text{wea}}\cap {A}_{\text{cap}}\cap {A}_{\text{wob}}\end{array}$$

The self-stability area index gives information about the damping of the system when all modes are stable.

4 Sensitivity analysis

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The aim of this research is to analyze the effect of the geometrical
parameters of the bicycle on the stability indices defined in the previous
section. This analysis is performed numerically by exploring the effect of
the various parameters by means of large series of simulations to assess the
sensitivity of the stability indices to the design parameters. The
sensitivity is analyzed combining two approaches. First, a variance-based
sensitivity method is used to explore the possible high-order interactions
between the design parameters that can affect the stability indices. Second,
a correlation analysis is used to investigate the main trend of the
variation in the stability indices associated with the change in each design
parameter across the whole domain. In both cases, eight design parameters
are considered: *r*_{R}, *r*_{F}, *m*_{H}, *x*_{B}, *z*_{B}, *w*, *c*, *λ*.

The analysis of the interactions of the different design parameters and their effect on the stability indices is performed through the variance-based method presented in Sobol (2001); Saltelli et al. (2008) and numerically implemented by Cannavo (2012). In the framework of this approach, two factors are said to interact when their contribution to the variance of the output cannot be expressed as the sum of their single contributions. In this paper, the importance of the interactions between variables on the stability indices is studied. To this aim, the contribution to the total variance of the single parameters (i.e., first-order interactions), and the contribution to the total variance of the pairs of parameters (i.e., second-order interactions) are calculated. When these contributions are calculated, the remaining variance is associated to higher-order interactions (i.e., third-order or higher).

For a design parameter *X*_{i}, the corresponding sensitivity index of its
effect on the output *Y* is calculated as the variance of the expectation of
*Y* conditional on *X*_{i} normalized by the unconditional variance of *Y*,
as presented in Eq. (5) (Saltelli, 2008).

$$\begin{array}{}\text{(5)}& {S}_{i}={\displaystyle \frac{V\left[E\left(Y\mathrm{|}{X}_{i}\right)\right]}{V\left(Y\right)}}\end{array}$$

For a pair of design parameters *X*_{i}, *X*_{j}, (with *i*≠*j*) the
corresponding sensitivity index of their effect on the output *Y* is
*S*_{ij}. This value is calculated as the normalized variance of the
expectation of *Y* conditional on *X*_{i} and *X*_{j} minus *S*_{i} and
*S*_{j}, as presented in Eq. (6).

$$\begin{array}{}\text{(6)}& {S}_{ij}={\displaystyle \frac{V\left[E\left(Y\mathrm{|}{X}_{i},{X}_{j}\right)\right]-V\left[E\left(Y\mathrm{|}{X}_{i}\right)\right]-V\left[E\left(Y\mathrm{|}{X}_{j}\right)\right]}{V\left(Y\right)}}\end{array}$$

For the numerical implementation of the method, a total of 40 000 points are used for the exploration of the domain and the evaluation of the sensitivity indices. Each parameter is sampled with a uniform probability density function, within the range defined by the lower and upper bounds presented in Table 2.

Figure 6 presents the contribution of first, second, and higher order
interactions, to the variance of the weave mode indices calculated by means
of the various bicycle models. The sum of the sensitivities of the weave
speed index (*v*_{wea}) to each single parameter (first-order interactions)
explains 93.5 % or more of the total variance. The model with the lowest
percentage of the total variance explained by the first-order interactions
is the complete model with the “hands-off” condition. For the same model,
it is found that the first-order sensitivities explain 90.3 % of the
total variance of the weave area index (*A*_{wea}).

Figure 7 summarizes the results of the sensitivity analysis for the capsize
mode indices, showing the contribution of the orders of interaction.
First-order interactions explain 97.8 % or more of the total variance of
the capsize speed index (*v*_{cap}). It is worth noticing that for the
complete model the capsize mode remains stable over the range of speed
considered (0 to 10 m s^{−1}). Even if capsize mode is stable, it is
possible to calculate the capsize area index (*A*_{cap}), which is related
to the damping of this mode. It is found that for the capsize area index the
complete bicycle model in “hands-on” condition has the lowest percentage
of the total variance explained by the first-order interactions (97.3 %).

Figure 8 shows the sensitivity of the wobble mode indices to the different
orders of interaction. The sum of the sensitivities explained by the
first-order interactions decreases for wobble, compared with those obtained
for the other two modes. For the wobble speed index (*v*_{wob}) the sum of
the first-order sensitivities explains 64.8 % of the total variance in
the case of the complete model in “hands-off” condition. When the WCBM
with CFA is used, the first-order interactions explain 88.8 % of the
total variance, whereas when the complete model in the “hands-on”
condition is adopted, 90.4 % of the total variance is associated to the
first-order interactions. For the wobble area index (*A*_{wob}), the
first-order interactions explain 85.8 % of the total variance when the
WCBM with CFA is used, 86.9 % when the full model in “hands-off”
condition is used, and 91.3 % when the full model in “hands-on”
condition is used. Regarding the effect of the second-order interactions on
*v*_{wob} and *A*_{wob}, the interaction between the two coordinates of the
location of the center of mass of the main body (*x*_{B}, *z*_{B}) is the
most relevant contribution for some models (i.e., over 5 %).

The analysis of the interactions of the design parameters with the global
stability indices is also performed by means of the variance-based method.
Figure 9 presents the contribution of first, second, and higher order
interactions to the variance of Ssr_{2} and SsA_{2}. For these indices,
the variances are mainly explained by the contribution of first order terms.
The model with the largest effect of second order and high order
interactions is the complete model with the “hands-off” condition, in this
case the first order interactions explain 93.3 % of the total variance of
Ssr_{2} and 89.6 % of the total variance of SsA_{2}.

Figure 10 shows the sensitivity of Ssr_{3} and SsA_{3} to the different
orders of interaction. The sum of the variances explained by the first-order
interactions is smaller for the 3-modes global stability indices than for
the 2-modes global stability indices. For the Ssr_{3}, the sum of the
first-order variances explains 62.2 % of the total variance in the case
of the complete model in “hands-on” condition. For the complete model in
“hands-off” condition, the first-order interactions explain 71.6 % of
the total variance, and for WCBM the with the CFA 75.9 % of the total
variance is associated to the first-order interactions. For SsA_{3}, the
first-order interactions explain 52.6 % of the total variance when the
complete model in “hands-on” condition is used, 70.4 % when the
complete model in “hands-off” condition is used, and 72.5 % when the
WCBM with CFA is used. Regarding the effect of the second-order interactions
on Ssr_{3} and SsA_{3}, the interaction between the radius of the front
wheel and the wheelbase (*r*_{F}, *w*) presents an important contribution
for the complete model (i.e., over 5 %), and the interaction between the
two coordinates of the location of the center of mass of the main body
(*x*_{B}, *z*_{B}) presents a relevant contribution for the WCBM with CFA.

The correlations associated to the single modes of vibration are studied one at a time considering both the speed index and the area index. A space-filling computational experiment is used, implementing a quasi-Monte Carlo exploration of the domain based on a Sobol low discrepancy sequence (Sobol, 1967). 40 000 points are evaluated, and the results are used for the computation of the correlation coefficients.

$$\begin{array}{}\text{(7)}& {\mathit{\rho}}_{xy}={\displaystyle \frac{{\mathit{\sigma}}_{xy}}{{\mathit{\sigma}}_{x}{\mathit{\sigma}}_{y}}}\end{array}$$

$$\begin{array}{}\text{(8)}& {\mathit{\sigma}}_{x}^{\mathrm{2}}={\displaystyle \frac{\mathrm{1}}{n}}{\sum}_{i=\mathrm{1}}^{n}({x}_{i}-\stackrel{\mathrm{\u203e}}{x}{)}^{\mathrm{2}}\end{array}$$

$$\begin{array}{}\text{(9)}& {\mathit{\sigma}}_{y}^{\mathrm{2}}={\displaystyle \frac{\mathrm{1}}{n}}{\sum}_{i=\mathrm{1}}^{n}({y}_{i}-\stackrel{\mathrm{\u203e}}{y}{)}^{\mathrm{2}}\end{array}$$

$$\begin{array}{}\text{(10)}& {\mathit{\sigma}}_{xy}={\displaystyle \frac{\mathrm{1}}{n}}{\sum}_{i=\mathrm{1}}^{n}({x}_{i}-\stackrel{\mathrm{\u203e}}{x})({y}_{i}-\stackrel{\mathrm{\u203e}}{y})\end{array}$$

In the present case, *σ*_{y} is the standard deviation of an output
(e.g., capsize speed), *y*_{i} are the values computed for all the
simulations, and $\stackrel{\mathrm{\u203e}}{y}$ is the arithmetic average of *y*_{i}. *σ*_{x} is the standard deviation of a design parameter (e.g., wheelbase),
*x*_{i} are the values of the parameter taken for the study, and $\stackrel{\mathrm{\u203e}}{x}$ is the arithmetic average of *x*_{i}. *σ*_{xy} is the covariance between an output and a design parameter. The correlation coefficient
represents the normalized measure of the strength of linear relationship
between variables, and ranges from −1 to 1. Values close to 1 indicate a
strong linear positive relationship between the variables; values close to
−1 indicate a strong linear negative relationship between them
(anti-correlation); values close or equal to 0 indicate no evidence of
linear relationship between variables.

Figures 11, 12, and 13 summarize the results of the correlation analysis. The correlation coefficients are shown in solid red when they represent positive correlations, and in dotted blue when they represent negative correlations. The circles that represent each correlation coefficient have an area that is proportional to the magnitude of the index.

Figure 11 presents the correlation coefficients related with the weave mode.
The basic WCBM shows that *c* and *r*_{F} have a strong correlation with the
weave speed index (*v*_{wea}), while *w* has a moderate correlation with
*v*_{wea}. When *r*_{F} increases *v*_{wea} decreases, which is a
stabilizing effect. For all the other parameters, the effect of an increment
is an increase in *v*_{wea}, which is a de-stabilizing effect. The analysis
of weave stability by means of the weave area index (*A*_{wea}) confirms the
previous results but shows two differences. The correlation between *x*_{B}
and *A*_{wea} is strong and shows a stabilizing effect. The correlation
between *r*_{F} and *A*_{wea} is weak. The inclusion of front assembly
compliance does not strongly modify *v*_{wea} and *A*_{wea}, there are only
minor variations in the values of the correlation coefficients. When the
full bicycle model is considered (with front assembly compliance and sliding
tires) most of the bicycle parameters roughly show the same effect on
*v*_{wea} and *A*_{wea} that they showed with the simpler models. The
exception is the effect of *x*_{B} and *λ* on *v*_{wea}, because with
the full model when these parameters increase, there is a decrease in
*v*_{wea} (stabilizing effect).

Therefore, as far as the weave mode is concerned, it can be stated that the predictions on weave stability made by the simplest models are confirmed when more complex models are adopted, there are only some variations in the relative importance of the various parameters.

All the previous results dealt with the hands-off condition, the full model makes it possible to study the hands-on condition as well. Positioning the rider's hands on the handlebar has a very small influence on the stability of the weave mode considering both the weave speed index and the weave area index.

Figure 12 makes it possible to analyze the effect of geometric parameters on
the stability of the capsize mode. The basic WCBM shows that *c*, *r*_{F},
and *x*_{B} have a strong correlation with the capsize speed index: an
increment in *r*_{F} has a de-stabilizing effect, because it decreases the
capsize speed, whereas increments on *x*_{B} or *c* have a stabilizing
effect. The analysis of capsize stability by means of the capsize area index
confirms the previous results but shows that *z*_{B} has a moderate
influence on capsize stability. The inclusion in the model of front assembly
compliance does not influence the capsize stability indices. Conversely, the
introduction of sliding tires in the bicycle model has a very large effect
on the capsize mode, which remains stable on the full range. The correlation
coefficients of the capsize area index calculated by means of the full model
with hands-on the handlebar are in good agreement with the correlation
coefficients calculated by means of the simpler models, only the effects of
*c*, *w* and *λ* are different. The simpler models present a strong
positive correlation of the capsize area and *c*, and the complete model has
only a weak correlation for the same pair. With the simpler models the
coefficients of *w* and *λ* show a weak positive correlation, whereas
with the full model the correlation coefficient of *w* is negative and
large, while the correlation coefficient of *λ* is negative but
negligible. The correlation analysis (carried out by means of the full
model) shows that the “hands-on” condition has negligible effect on
capsize stability.

Finally, the effect of geometric parameters on wobble stability is analyzed
by means of the correlation coefficients that are shown in Fig. 13. The 2
DOF WCBM does not simulate the wobble mode and the simplest model predicting
wobble is the WCBM with CFA. With this model, the parameter with the
strongest positive correlation coefficient with *v*_{wob} is *w*, followed by *x*_{B}, which has a moderate correlation; the parameter *m*_{H} has a
negative correlation coefficient (de-stabilizing effect). The correlation
coefficients of *A*_{wob} calculated by means of the same model have a
similar trend, with only two noticeable differences: a moderate negative
correlation coefficient of *r*_{F} with *A*_{wob}, and an increased positive
correlation coefficient of *c* with *A*_{wob}. When the sliding behavior of
tires is considered, there are two phenomena that are independently able to
generate a wobble mode: front assembly compliance (Doria et al., 2017) and
tire model with relaxation length (Sharp, 2008). Correlation coefficients of
*v*_{wob} and geometric parameters calculated by means of the hands-off
model show that the most influential parameters have the same effect on
wobble stability they showed with the WCBM with CFA. Only parameter *x*_{B}
has a different effect on wobble stability with a negligible correlation
with wobble speed. Correlation analysis between *A*_{wob} and the geometric
parameters shows results very similar to the ones obtained with the WCBM
with CFA, only the correlation coefficient of *x*_{B} is weaker but it
maintains the same sign. Correlation analysis carried out with the full
model with hands-on the handlebar shows some differences with respect to the
hands-on case, but all the parameters maintain the same effect on stability.

The correlation between the geometric parameters and the indices that define
the global stability of the bicycle can be considered the most important
result from the practical point of view. The key question is if the
predictions made by the simpler models hold true even when more realistic
bicycle models are considered. The WCBM can predict only weave and capsize
stability, therefore indices Ssr_{2} and SsA_{2} are considered.
Figure 14 shows that the predictions made by the WCBM hold true when front
assembly compliance is included in the model. The scenario drastically
changes when the effect of tires is taken into account. In this case only
the correlation coefficients of Ssr_{2} and SsA_{2} with *x*_{B}, *z*_{B}, and *w* maintain the same sign they showed with the WCBM, even if
some of them have an important change in magnitude. This phenomenon takes
place because in the presence of sliding tires the capsize mode is stable
over the full range of forward speeds here considered (see Fig. 4) and the
self-stability range actually depends only on the weave speed. Therefore,
some geometric parameters (like *r*_{F} and *c*), which in the WCBM have
important and opposite effects on *v*_{wea} and *v*_{cap}, influence only
*v*_{wea} when the full model is used. In the WCBM trail *c* has a
de-stabilizing effect on weave, because it increases *v*_{wea} (see Fig. 11), and a stabilizing effect on capsize, because it increases *v*_{cap}
(see Fig. 12), the latter effect being stronger thus the self-stability
range increases with *c*. Conversely, in the full model *c* increases
*v*_{wea} (de-stabilizing effect) but it has no effect on *v*_{cap}, hence
the self-stability range decreases if *c* increases. A similar argument
holds true for the effect of *r*_{F}. The self-stability range of weave and
capsize slightly changes if the full model with hands-on is considered.
Figure 14 also shows that the geometric parameters influence the SsA_{2}
index roughly in the same way they influence Ssr_{2}.

The simplest model that can be used for calculating the self-stability indices taking into account three modes (weave, capsize, and wobble) is the WCBM with front compliance, see Fig. 15.

Correlation analysis shows that in this case parameter *x*_{B} has the
highest stabilizing effect followed by *w* and *c*, whereas parameter
*z*_{B} has the highest destabilizing effect followed by *m*_{H} and
*r*_{F}. When tire sliding is included in the model, parameters *m*_{H}, *z*_{B}, and *w* maintain their correlations on Ssr_{3} and SsA_{3},
only with small changes in magnitude. Parameter *x*_{B} reduces its
correlations with Ssr_{3} and SsA_{3}, whereas parameter *c* changes
the sign of its correlations with Ssr_{3} and SsA_{3}. When the tire
sliding is included, the importance of *r*_{F} grows and takes on a strong
stabilizing effect. On the one hand, tire properties did not show a very
large influence on *v*_{wob} and *A*_{wob} (see Fig. 13). On the
other hand, when tire sliding is included in the model the correlation
coefficients of *c* and *r*_{F} show similar changes in both the stability
of two and three modes. Therefore, it may be concluded that these phenomena
are mainly related to capsize and weave stability. Actually, Figs. 3 and 4 show that the large differences in the stability range and area that take
place when tire sliding is considered are mainly due to the modifications in
the loci of capsize and weave. Finally, the full model makes it possible to
analyze the effect of geometric parameters on Ssr_{3} andSsA_{3}
with hands-on the handlebar. There are not large differences with respect to
the hands-off case, but parameter *x*_{B} with hands-on has a weak
de-stabilizing effect.

The comparison between the stability indices calculated with 2 and 3 modes
shows that some parameters change their effect on stability: with 3 modes
the increase in *w* has a strong stabilizing effect, instead of the weak
de-stabilizing effect that it has with 2 modes; additionally, with 3 modes
the increase in *m*_{H} has a weak de-stabilizing effect, instead of the
negligible effect that it has with 2 modes. This phenomenon is due to the
large effect of *w* and *m*_{H} on wobble stability (see Fig. 13).

5 Conclusion

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When the basic WCBM is extended by introducing front assembly compliance,
the most important effect is the appearance of a high frequency wobble mode,
which may become unstable at the highest speeds considered in the framework
of this research (i.e., 10 m s^{−1} for a city bicycle). Nevertheless, the
stability features of weave and capsize are not strongly modified and the
effects of the geometric and mass properties on the stability of these modes
that are predicted by the WCBM still hold true. The analysis of the global
stability indices (Ssr and SsA) shows that some parameters (*m*_{H},
*w*) have an effect on the global stability of the three modes opposite to
the one they showed in the WCBM, considering only weave and capsize modes.
This happens because *m*_{H} and *w* has a strong effect of wobble
stability.

The introduction of tire slip in the model has an important effect on
stability, because not only the wobble mode appears, but also the capsize
mode becomes stable over the whole range of speeds. Therefore, even if the
influence of the various geometric and mass properties on the stability of
the single modes (weave and capsize) is very similar to the one predicted by
the WCBM, the effect on global stability is often different. This phenomenon
takes place because some parameters have opposite effects on the stability
of weave and capsize and in the simple WCBM their effect on global stability
derives from a combination of the effects they have on the single modes.
Conversely, in the presence of tire slip, the capsize mode is always stable
and no longer relevant, thus the combined effects do not take place, and
global stability is dominated by the weave and wobble modes. Only parameters
*x*_{B} and *z*_{B} maintain the effect of stability they showed in the WCBM.

A different posture of the rider with hands-on the handlebar does not
strongly change the effect of mass and geometric parameters on the stability
indices. The most important effect is that with hands-on *x*_{B} has a small
de-stabilizing effect.

According to the presented results, it is possible to state that the simple WCBM gives useful hints for understanding the physical phenomena determining bicycle stability, especially at low speed. The simpler models give more accurate information about the stability of the single modes than about the global stability of the bicycle; therefore they can be useful when the stability of a single mode is the main concern, because the other modes can be stabilized by the rider, or become unstable at very high speed. Generally speaking, a full bicycle model is strongly recommended for studying the global stability properties of actual bicycles.

Data availability

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Data availability.

All the data used in this manuscript can be obtained by request from the corresponding author.

Author contributions

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Author contributions.

AD coordinated the research activity and analyzed the results. SR developed the numerical codes and carried out the simulations. LM developed the correlation analysis and analyzed the results.

Competing interests

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Competing interests.

The authors declare that they have no conflict of interest.

Financial support

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Financial support.

This research has been partially supported by the Colombian Administrative Department of Science, Technology, and Innovation (Colciencias) (grant no. Doctorate Formation Program 617 of 2013).

Review statement

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Review statement.

This paper was edited by Anders Eriksson and reviewed by James Sadauckas and one anonymous referee.

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Short summary

A simple bicycle model considers only geometric and mass properties. Bicycle models considering compliance, tires, and rider posture are available. For the designer, it is important to know if the effect of geometric and mass properties on stability is correctly predicted by a simple bicycle model. Stability indices are calculated by means of bicycle models of increasing complexity. Results show that the simple model correctly predicts only the stability of the single modes.

A simple bicycle model considers only geometric and mass properties. Bicycle models considering...

Mechanical Sciences

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