# Artificial Knee Joints Actuators with Energy Recovery Capabilities: A Comparison of Performance

Authors: Roberta Alò; Francesco Bottiglione; Giacomo Mantriota
Journal: Journal of Robotics
 (2016)

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## Abstract

The human knee absorbs more energy than it expends in level ground walking. For this reason it would be useful if the actuation system of a wearable robot for lower limbs was able to recover energy thus improving portability. Presently, we recognize three promising technologies with energy recovery capabilities already available in the literature: the Series Elastic Actuator (SEA), the Clutchable Series Elastic Actuator (C-SEA), and the flywheel Infinitely Variable Transmission (F-IVT) actuator. In this paper, a simulation model based comparison of the performance of these actuators is presented. The focus is on two performance indexes: the energy consumed by the electric motor per gait and the peak torque/power requested to the electric motor. Both quantities are related to the portability of the device: the former affects the size of the batteries for a given desired range; the latter affects the size and the weight of the electric motor. The results show that, besides some well-explained limitations of the presented methodology, the C-SEA is the most energy efficient whereas the F-IVT allows cutting down the motor torque/peak power strongly. The analysis also leads to defining how it is possible to improve the F-IVT to achieve a reduction of the energy consumption.


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## Body

## 1. Introduction

In the human normal gait cycle, the knee joint undergoes phases of positive and negative work. Therefore an optimally designed wearable device for lower limbs (orthoses, exoskeletons, and prostheses) should be able to store energy during the phases of negative work and to permit reusing it when required. Indeed, one of the greatest limits to the development of powered orthoses, exoskeletons, and prostheses deals with their portability that is often limited by the lack of actuators and energy sources enabling the development of devices with both reasonable weight and an acceptable range of locomotion [1]. The energy recovery during normal operation is a smart strategy to reduce the net energy consumption. It could extend the portability of wearable devices enlarging their operating range and reducing the power requested to the motor.Most of the wearable devices for lower limbs rely on battery-powered electric motors [2]. Reversibility of the electric drives permits in principle the regeneration of electric energy to be stored in a battery pack. However, in the context of wearable robots for lower limbs, the charging/discharging cycles of the battery occur under variable tension/current conditions and their frequency is relatively high, resulting in a very large number of cycles during the lifetime of the device, which adversely affects the performance and the life of the battery [3, 4]. The relatively low efficiency of the mechanical to electrical energy conversion and of the battery charge/discharge process and the high frequency of the gait cycle are the reasons why the electric energy recovery has not usually been considered in this kind of application [5, 6] up to very recent times [7].Great efforts are focused on developing mechanical energy storage devices, in which the lack of any energy conversion would result in a greater efficacy. SEAs (Series Elastic Actuators) include an elastic element between the motor and the load which stores energy and delivers peak power values greater than the maximum power of the motor, and it offers greater shock tolerance, lower reflected inertia, and more accurate and stable force control [8–11]. In SEAs, the linear torque-angle relationship of the early stance knee flexion-extension phase of human walking can be rendered only by a spring whose stiffness is equal to the slope of the torque-angle curve. VSAs (Variable Stiffness Actuators) which adapt their stiffness to match the torque-angle curve also during the swing-phase [12] are claimed to achieve greater energy saving and peak power decrease compared to SEAs. Furthermore VSAs are able to adjust the optimal value of their stiffness according to the load conditions, permitting obtaining greater benefits at more than one specific walking gait.In SEAs, when only the spring powers the knee joint, the motor must provide only reactionary torque at negligible motor speed, thus working inefficiently [7]. This consideration motivated the improvement of the design of SEAs into the development of the C-SEA (Clutchable Series Elastic Actuator), where a clutch is activated or deactivated according to the phase of the gait cycle. The C-SEA is explained in detail in [7], where its performance is evaluated in powering knee prostheses. It was proved that the C-SEA reduces the net electric energy consumption also thanks to the electric energy recovery. However, a limitation of such device is that when the clutch is activated the motor is not able to provide additional torque; thus the stiffness of the spring limits the operation of the C-SEA mechanism to those activities whose torque demand is into the bandwidth of the device, which is defined by the stiffness value.Another way to store mechanical energy involves kinetic energy storage in a high speed rotating mass (flywheel). The flywheel energy storage has been recently reconsidered in the automobile field under the denomination of mechanical KERS (Kinetic Energy Recovery System). It is one possible short-term solution to achieve an improvement of the fuel economy performance of automobiles. In mechanical KERS, the energy is moved from the load (vehicle) to the flywheel under negative work phases and from the flywheel to the load otherwise [13] with no energy transformation. Inspired by KERS, the F-IVT (flywheel-IVT) actuator has been presented by the authors [14] as a device leading to potential benefits when employed in powering knee bionic joints. The F-IVT includes a brushless DC motor, a flywheel, an IVT (Infinitely Variable Transmission), and HD (harmonic drive) gear. The flywheel acts as a kinetic energy storage device; energy is moved between the motor and the joint thanks to a proper change of the speed ratio of the IVT. The IVT, whose ratio changes between positive and negative values, also permits a nearly constant motor speed, while the desired joint speed is, in principle, always matched.In [14] the performance of the F-IVT was predicted in one specific walking condition, for which it was optimally designed. The authors proved that the F-IVT architecture permits undersizing the electric motor, which in F-IVT delivers an almost constant power value roughly equal to the mean power requested and by far less than the peak power. Moreover, the electric motor can be sized for working at a nearly fixed point at the greatest efficiency values, with a resulting potential saving of electric energy consumption. The motor undersizing would be a great advantage in this kind of application because it facilitates the portability of the device, also enlarging its operating range.However, the results described in [14] give a limited insight into the F-IVT potential because the performance is therein estimated in the nominal working condition, that is, the one taken as a reference to optimally design the F-IVT components. Indeed, the portable lower limb wearable robots are required to support the wearer in his daily activity; thus their actuators do not usually work under the nominal condition.The aim of this analysis is to further investigate the F-IVT by predicting its performance when it does not work under the condition for which it was optimally designed, like different walking speeds and stairs climbing. The energy and power requirements of the F-IVT were estimated through a model based approach and compared with those of two very efficient actuators already used in biomechatronics devices, the SEA and the C-SEA, in order to evaluate if it could be a competitive actuator for artificial knee joints of wearable robots.


## 2. Materials and Methods

This study compares through a model based approach three different actuators for powering artificial knee joints: the F-IVT, a novel actuator presented very recently in [14], and two other high performance actuators, the SEA and the C-SEA, which were largely investigated in previous works [3, 7, 15, 16].The actuators F-IVT, SEA, and C-SEA were compared in different working conditions: level ground walking at different speeds (0.5, 1.1, 1.6, and 2.1 m/s) and stairs climbing at different inclinations (24°, 30°, and 42°). These conditions often recur in daily life. Indeed, it would be desirable for any actuator of artificial human joints to support the subject in his daily activity, requiring both a large operating range and the portability of the device.Two main performance indexes have been taken into consideration for comparison: the energy consumption (per gait) and the peak of electric power, both calculated at the motor electrodes. These are significant quantities for the development of lightweight and portable wearable robots because they affect the size and the weight of the actuator, as well as the operating range of the device. The energetic and power requirements of all the actuators were calculated through an inverse dynamic approach, that is to say, starting from the load characteristics (knee angle and torque versus time) given as input data to the model provided in Sections2.1–2.3. Gait cycles data were taken from [17, 18] (Figure 1).Figure 1
Gait cycle analysis data of the knee joint (angle, torque, and power) in level ground walking at different speeds and in stairs climbing at different inclinations. Data were adapted from [17, 18].
(a)
(b)
(c)The following sections provide details on the working principle of all the actuators, as well as on their mathematical modeling and the sizing procedure. Both SEA and C-SEA were modeled and sized as already done in the literature.


### 2.1. The Flywheel-IVT (F-IVT) Actuator

The F-IVT is an innovative actuator with energy recovery capabilities to power artificial knee joints [14]. It is made up of the following devices: a brushless DC motor, a flywheel, an IVT, and a HD gear (Figure 2). The brushless DC motor and the HD gear are often employed in biomechatronics: the first one because of its great efficiency with respect to other electric drives [19], the second one because of its large torque capacity, high gear ratios (τ
H
D), and small size [19]. The flywheel and the IVT are introduced for the first time in an actuation system of artificial leg joints with the aim of recovering energy and reducing the irregularity of the motor working point.Figure 2
Fluxes of power in the F-IVT under forward, reverse, and irreversible motion conditions. The arrows indicate the power flows direction in each of them (P
M motor power, P
F rate of change of the kinetic energy of the flywheel, P
L power losses in the transmission devices, and P
K knee power).As in a mechanical KERS (Kinetic Energy Recovery System) [13], in the F-IVT the flywheel operates as a kinetic energy storage device in which energy is stored when the power demand of the knee is negative (reverse motion) and it is released otherwise (forward motion), as schematically depicted in Figure 2. Energy is moved between the motor and the joint through a proper change of the speed ratio of the Continuously Variable Transmission. More specifically, an IVT is required because of the alternate motion of the knee joint. The speed ratio of the IVT (τ
I
V
T) is changed continuously between positive and negative values (τ
I
V
T
m
i
n
≤
τ
I
V
T
≤
τ
I
V
T
m
a
x) permitting achieving the desired joint speed (ω
K) while the motor speed is nearly constant (ω
M
=
ω
K
/
τ
I
V
T
τ
H
D) even when the output speed is zero thanks to the neutral gear condition of the IVT. An IVT with shunted CVT architecture was considered in the F-IVT actuator, because mathematical models of its efficiency are well established in the literature [20–22]. It is furthermore assumed that the speed ratio of the IVT is always perfectly regulated in order to be equal to the required value of τ
I
V
T at each instant of the gait cycle.The operation of the F-IVT is such that the motor works at nearly fixed point with high efficiency and with a resulting possibility of undersizing the motor. Indeed, in the F-IVT the motor must provide an almost constant power, while the flywheel provides the variations of the requested power at the knee joint, permitting satisfying the following instantaneous power balance equation:(1)
P
K
=
P
M
+
P
F
+
P
L
,where P
K is the knee power, P
M is the motor power, P
F (P
F
=
-
J
F
ω
˙
M
ω
M) is the rate of change of the kinetic energy of the flywheel of inertia J
F, which rotates with the same motor angular speed (ω
M) and acceleration (ω
˙
M), and P
L is the power lost in the transmission devices.With the motor speed being nearly constantω
M
≈
ω
-
M (ω
-
M is the average velocity of the motor), in order to achieve an almost constant power delivery, the motor is supposed to be torque controlled with constant torque C
M given by(2)
C
M
=
1
T
ω
-
M
∫
0
T
P
K
t
-
P
L
t
d
t
,where T is the period of the gait cycle, ω
-
M is the mean value of the motor angular speed, and ∫
0
T
P
K
t
-
P
L
(
t
)
d
t is the total amount of energy that the motor must provide to fulfill the knee power requirement and to overcome the power lost in the transmission devices.Detailed efficiency models were adopted for the IVT and for the HD to realistically estimate the power losses.P
L (see (1)) can be written as a function of the instant values of the efficiency of the IVT (η
I
V
T) and the HD gear (η
H
D) in forward (P
L
=
-
1
-
η
I
V
T
η
H
D
P
M
+
P
F) and reverse (P
L
=
-
1
-
η
I
V
T
η
H
D
P
K) motion. The adopted efficiency models also consider the nonreversible motion condition, which implies that P
M, P
F, and P
K are all delivered to the transmission and then dissipated as heat losses (Figure 2). This situation can involve the HD, the IVT, or both simultaneously, depending on the actual values of speed and torque. In particular, we adopted the model given in [20] (described in detail in Appendix A) for predicting η
I
V
T (Figure 3(a)), and we always referred to the guidelines of the data sheet of HD gears given by one manufacturer (AG Harmonic Drive) to estimate η
H
D (Figure 3(b)) in this paper.Figure 3
Efficiency maps of the IVT (a) and of the HD gear (b) obtained through detailed efficiency models which distinguish the performance of the transmission devices in forward (P
O
U
T
≥
0), revrse (P
O
U
T
<
0), and irreversible motion conditions. In (a) η
I
V
T is given as a function of τ
I
V
T whereas η
H
D is given as a function both of the output motor speed and of the torque at the output shaft normalized to the Rated Torque (RT) of the HD gear selected.
(a)
(b)To determine the actual working conditions of the actuator, the equations given above are solved through an iterative routine (Figure4) aimed at calculating the mechanical motor quantities ω
M, ω
˙
M, C
M. The iterative calculation is necessary to find the actual value of the motor speed, which is not known a priori. Starting from a guess value of constant motor speed ω
M
(
0
), the corresponding values of C
M (see (2)) and then of ω
˙
M (from (1)) are calculated. ω
˙
M is then integrated through a numerical method (Newton-Raphson method) to find ω
M
(
1
). At integration step j, an error is defined as E
R
R
j
=
(
1
/
T
)
∫
0
T
(
ω
M
(
j
+
1
)
-
ω
M
(
j
)
)
2
d
t. The iteration stops when E
R
R
j
≤
E
R
R
m
a
x, where E
R
R
m
a
x is the error tolerance, and it is requiring also that the constraint on the IVT ratio is satisfied (τ
I
V
T
m
i
n
≤
τ
I
V
T
≤
τ
I
V
T
m
a
x).Figure 4
Schematic representation of the iterative routine to solve to calculate the mechanical motor requirements (ω
M
,
C
M).After the mechanical motor requirements are defined, the electric power requested to the motor (P
E
L
=
v
M
i
M) is calculated as a function of the motor parameters (motor torque constant k
t, damping friction coefficient ν, Coulomb friction torque C
f
r, motor resistance R, back EMF constant k
e
m
f, and motor inertia J
M) and of the calculated requirements (motor torque C
M, angular motor speed ω
M, and angular motor acceleration ω
˙
M):(3)
i
M
=
C
M
k
t
+
J
M
ω
˙
M
k
t
+
ν
ω
M
k
t
+
sign
⁡
ω
M
C
f
r
k
t
,
v
M
=
R
i
M
+
k
e
m
f
ω
M
,where i
M and v
M are, respectively, the electric motor current and voltage.Finally, the electric energy to be supplied is calculated as the time integral of the motor electric powerP
E
L
=
v
M
i
M in the gait cycle; thus the energy consumption of all the electronic modules was neglected. According to [23], in the reverse operation it may happen that the electric motor is not able to generate electricity. In those cases, P
E
L
=
0. Consider(4)
E
E
L
=
∫
0
T
P
E
L
d
t
.The mathematical model of the F-IVT given above (see (1)–(4)) is implemented to estimate the performance of the F-IVT. In this work the F-IVT sizing was carried on in such a way that it is capable of powering the knee joint under different locomotion regimes, namely, the level ground walking at different speeds and the stairs climbing at different inclinations. In particular, the size of the HD gear and that of the motor were determined from the maximum power requested considering all possible walking regimes, whereas the most frequent one (level ground walking at 1.1 m/s) was used to optimally design the F-IVT in order to make it work very efficiently most of the time. More details about the criterion followed to size each component of the F-IVT, the nominal values of which are listed in Table 1, can be found in Appendix B.Table 1
Model parameters of the actuators F-IVT, SEA, and C-SEA. The motor damping parameters and the Coulomb friction torque are not provided by data sheet, but they were estimated following the guidelines given by Maxon.
F-IVT
SEA
C-SEA
Brushless motor
Model
EC-max 40283871
EC 60167131
EC 45136209
C
f
r [mNm]
5.2
0.8
0.77
J
M [g cm2]
101
831
209
k
e
m
f [V/rad/s]
0.0628
0.147
0.0739
k
t [mNm/A]
62.8
147
73.9
R [Ω]
2.02
1.03
1.01
ν [Nm/rad/s]
8.66
·
10
-
6
1.4
·
10
-
4
2.7
·
10
-
5
i
C
[A]
—
0.25
v
C
[V]
—
24
Flywheel
J
v [g cm2]
5
·
10
3
—
—
IVT
τ
I
V
T
[−1.35, 1.21]
—
—
Gear train
τ
G
T
1/50
1/80
1/143
η
G
T
By model
By model
0.9
Spring
K [Nm/rad]
—
375.14
250


### 2.2. Series Elastic Actuator (SEA)

SEAs have been extensively employed in wearable devices for lower limbs. In SEAs a spring is put in series between the motor and the artificial powered joint (Figure5(a)). The elastic element gives advantages to the actuation system such as increasing of shock tolerance and limited high frequency actuator impedance and energy storage [8–10]. Since the force/displacement characteristic of the spring is linear, the SEA is very efficient in powering the knee joint because it can be designed to take advantage of the linear torque-angle (or spring-like) relationship of the knee in the early stance flexion-extension phase of level ground walking. In particular if the stiffness of spring (K) is chosen equal to the slope of the torque-angle curve, the spring alone would render the spring-like relationship, resulting in a great reduction of the motor mechanical energy requirement.Figure 5
Schematic pictures of the SEA (a) and C-SEA (b).
(a)
SEA
(b)
C-SEAIn this work the electric power and energy requirement of SEA to power knee joint in level ground walking at different speeds and in stairs climbing at different inclinations are calculated through (3)-(4) as a function of angle (ϑ
M
=
C
K
/
K
+
ϑ
K
1
/
τ
G
T, τ
G
T being speed ratio of the gear train) and torque (C
M
=
C
K
τ
G
T
/
η
G
T, η
G
T being efficiency of the gear train) requirements of the SEA motor.As done for the F-IVT, the SEA was also sized to power the knee joint even under the most powerful condition examined and it was optimized according to the most frequent one. In particular the most powerful condition leads to the choice of both the motor and the HD, whereas the most frequent one leads to the choice of series stiffness which minimizes the energy consumption. In our calculations we used the same walking cycles of [17] so also the optimal value of the stiffness coefficient of the spring is the one determined in [17].According to [24], the gear train of the SEA comprises a harmonic drive gear (HD). The value of gear ratio of the HD is larger for SEA than for the F-IVT to reduce the maximum torque value requested to the motor and thus to limit the motor size. This choice leads to an average efficiency of the HD that is smaller than that in the F-IVT. The selected 400 W brushless Maxon Motor (model: EC 60 p.n. 167131) is able to provide the maximum torque requested to the motor (C
M
m
a
x
=
1.494 Nm) while working under the motor speed limit (ω
M
m
a
x
=
7322 rpm). We noticed that this motor is too heavy for a proficient use in a wearable device, but, on the other hand, it is the only one allowing the SEA to power the knee in all the conditions examined. The model parameters adopted are listed in Table 1.


### 2.3. Clutchable Series Elastic Actuator (C-SEA)

The C-SEA (Figure5(b)) was developed to overtake one limit of SEAs related to the inefficiency of the motor in the stance phase [7]. In fact, even if SEAs greatly reduce the motor mechanical energy requirement in the stance phase when the spring alone powers the knee joint, the electric motor works at very slow speeds and thus very inefficiently. The C-SEA improved the design of SEAs by including a clutch on the motor shaft that is conveniently activated or deactivated according to the cycle phase. In particular during the spring-like phase of the gait cycle the clutch is activated and the spring renders the complete torque-angle relationship while the motor is required to supply only reactionary torque; during the other phases of the cycle, the clutch is deactivated and the C-SEA works as a SEA.Similar equations as those of SEAs govern the operation of the C-SEA. The complete set of equations given in [7] follows:(5)
C
M
=
C
K
τ
G
T
η
G
T
clutch  off
0
clutch  on
,
ϑ
M
=
C
K
K
+
ϑ
K
1
τ
G
T
clutch  off
0
clutch  on
,
i
M
=
C
M
k
t
+
J
M
ω
˙
M
k
t
+
ν
ω
M
k
t
+
sign
⁡
ω
M
C
f
r
k
t
clutch  off
i
C
clutch  on
,
v
M
=
R
i
M
+
k
e
m
f
ω
M
clutch  off
v
C
clutch  on
,where i
C is the clutch current and v
C is the clutch voltage when the clutch is activated.In this work the authors estimated the electric energy and power consumption of the C-SEA in level ground walking at different speeds and in stairs climbing at different inclinations. The mathematical model and many of the parameters of [7] were adopted to calculate the performance of C-SEA. However, because of the different reference gait cycle data some characteristics have been changed and a bigger electric motor was selected. A 250 W brushless Maxon Motor (model: EC 45 p.n. 136209, parameters in Table 1) was chosen because it is able to provide a peak torque compatible with the maximum required (C
M
m
a
x
=
0.323 Nm) in the locomotion regime explored and the maximum motor speed (ω
M
m
a
x
=
11574 rpm) is always below the motor speed limit. The optimal spring stiffness value (K) was also not the same as [7] because of the different gait cycles data considered in this work. In particular, the optimal spring stiffness in [7] is defined as the one which minimizes the kinematic similarity defined as(6)
Ψ
=
∫
ϑ
C
S
E
A
-
ϑ
K
2
d
t
,where ϑ
C
S
E
A is the output displacement of the C-SEA and ϑ
K is the output displacement of the knee joint. Such criterion was adopted by Rouse et al. in [7] because they proved that the stiffness of the spring does not affect the electrical power profiles but determines very different knee kinematics. Indeed, when the stiffness affects the knee angle displacement, the clutch absorbs a nearly constant electrical power. Based on this minimization criterion, we calculated an optimal stiffness value of 250 Nm/rad, at which the kinematic agreement was of 8
·
10
-
4 rad2 s (Figure 6).Figure 6
Kinematic similarity (Ψ) as a function of series stiffness averaged across walking speeds for subject weight of 75 kg. The minimum value of Ψ is kept approximately at the series stiffness value of 250 Nm/rad.


## 2.1. The Flywheel-IVT (F-IVT) Actuator

The F-IVT is an innovative actuator with energy recovery capabilities to power artificial knee joints [14]. It is made up of the following devices: a brushless DC motor, a flywheel, an IVT, and a HD gear (Figure 2). The brushless DC motor and the HD gear are often employed in biomechatronics: the first one because of its great efficiency with respect to other electric drives [19], the second one because of its large torque capacity, high gear ratios (τ
H
D), and small size [19]. The flywheel and the IVT are introduced for the first time in an actuation system of artificial leg joints with the aim of recovering energy and reducing the irregularity of the motor working point.Figure 2
Fluxes of power in the F-IVT under forward, reverse, and irreversible motion conditions. The arrows indicate the power flows direction in each of them (P
M motor power, P
F rate of change of the kinetic energy of the flywheel, P
L power losses in the transmission devices, and P
K knee power).As in a mechanical KERS (Kinetic Energy Recovery System) [13], in the F-IVT the flywheel operates as a kinetic energy storage device in which energy is stored when the power demand of the knee is negative (reverse motion) and it is released otherwise (forward motion), as schematically depicted in Figure 2. Energy is moved between the motor and the joint through a proper change of the speed ratio of the Continuously Variable Transmission. More specifically, an IVT is required because of the alternate motion of the knee joint. The speed ratio of the IVT (τ
I
V
T) is changed continuously between positive and negative values (τ
I
V
T
m
i
n
≤
τ
I
V
T
≤
τ
I
V
T
m
a
x) permitting achieving the desired joint speed (ω
K) while the motor speed is nearly constant (ω
M
=
ω
K
/
τ
I
V
T
τ
H
D) even when the output speed is zero thanks to the neutral gear condition of the IVT. An IVT with shunted CVT architecture was considered in the F-IVT actuator, because mathematical models of its efficiency are well established in the literature [20–22]. It is furthermore assumed that the speed ratio of the IVT is always perfectly regulated in order to be equal to the required value of τ
I
V
T at each instant of the gait cycle.The operation of the F-IVT is such that the motor works at nearly fixed point with high efficiency and with a resulting possibility of undersizing the motor. Indeed, in the F-IVT the motor must provide an almost constant power, while the flywheel provides the variations of the requested power at the knee joint, permitting satisfying the following instantaneous power balance equation:(1)
P
K
=
P
M
+
P
F
+
P
L
,where P
K is the knee power, P
M is the motor power, P
F (P
F
=
-
J
F
ω
˙
M
ω
M) is the rate of change of the kinetic energy of the flywheel of inertia J
F, which rotates with the same motor angular speed (ω
M) and acceleration (ω
˙
M), and P
L is the power lost in the transmission devices.With the motor speed being nearly constantω
M
≈
ω
-
M (ω
-
M is the average velocity of the motor), in order to achieve an almost constant power delivery, the motor is supposed to be torque controlled with constant torque C
M given by(2)
C
M
=
1
T
ω
-
M
∫
0
T
P
K
t
-
P
L
t
d
t
,where T is the period of the gait cycle, ω
-
M is the mean value of the motor angular speed, and ∫
0
T
P
K
t
-
P
L
(
t
)
d
t is the total amount of energy that the motor must provide to fulfill the knee power requirement and to overcome the power lost in the transmission devices.Detailed efficiency models were adopted for the IVT and for the HD to realistically estimate the power losses.P
L (see (1)) can be written as a function of the instant values of the efficiency of the IVT (η
I
V
T) and the HD gear (η
H
D) in forward (P
L
=
-
1
-
η
I
V
T
η
H
D
P
M
+
P
F) and reverse (P
L
=
-
1
-
η
I
V
T
η
H
D
P
K) motion. The adopted efficiency models also consider the nonreversible motion condition, which implies that P
M, P
F, and P
K are all delivered to the transmission and then dissipated as heat losses (Figure 2). This situation can involve the HD, the IVT, or both simultaneously, depending on the actual values of speed and torque. In particular, we adopted the model given in [20] (described in detail in Appendix A) for predicting η
I
V
T (Figure 3(a)), and we always referred to the guidelines of the data sheet of HD gears given by one manufacturer (AG Harmonic Drive) to estimate η
H
D (Figure 3(b)) in this paper.Figure 3
Efficiency maps of the IVT (a) and of the HD gear (b) obtained through detailed efficiency models which distinguish the performance of the transmission devices in forward (P
O
U
T
≥
0), revrse (P
O
U
T
<
0), and irreversible motion conditions. In (a) η
I
V
T is given as a function of τ
I
V
T whereas η
H
D is given as a function both of the output motor speed and of the torque at the output shaft normalized to the Rated Torque (RT) of the HD gear selected.
(a)
(b)To determine the actual working conditions of the actuator, the equations given above are solved through an iterative routine (Figure4) aimed at calculating the mechanical motor quantities ω
M, ω
˙
M, C
M. The iterative calculation is necessary to find the actual value of the motor speed, which is not known a priori. Starting from a guess value of constant motor speed ω
M
(
0
), the corresponding values of C
M (see (2)) and then of ω
˙
M (from (1)) are calculated. ω
˙
M is then integrated through a numerical method (Newton-Raphson method) to find ω
M
(
1
). At integration step j, an error is defined as E
R
R
j
=
(
1
/
T
)
∫
0
T
(
ω
M
(
j
+
1
)
-
ω
M
(
j
)
)
2
d
t. The iteration stops when E
R
R
j
≤
E
R
R
m
a
x, where E
R
R
m
a
x is the error tolerance, and it is requiring also that the constraint on the IVT ratio is satisfied (τ
I
V
T
m
i
n
≤
τ
I
V
T
≤
τ
I
V
T
m
a
x).Figure 4
Schematic representation of the iterative routine to solve to calculate the mechanical motor requirements (ω
M
,
C
M).After the mechanical motor requirements are defined, the electric power requested to the motor (P
E
L
=
v
M
i
M) is calculated as a function of the motor parameters (motor torque constant k
t, damping friction coefficient ν, Coulomb friction torque C
f
r, motor resistance R, back EMF constant k
e
m
f, and motor inertia J
M) and of the calculated requirements (motor torque C
M, angular motor speed ω
M, and angular motor acceleration ω
˙
M):(3)
i
M
=
C
M
k
t
+
J
M
ω
˙
M
k
t
+
ν
ω
M
k
t
+
sign
⁡
ω
M
C
f
r
k
t
,
v
M
=
R
i
M
+
k
e
m
f
ω
M
,where i
M and v
M are, respectively, the electric motor current and voltage.Finally, the electric energy to be supplied is calculated as the time integral of the motor electric powerP
E
L
=
v
M
i
M in the gait cycle; thus the energy consumption of all the electronic modules was neglected. According to [23], in the reverse operation it may happen that the electric motor is not able to generate electricity. In those cases, P
E
L
=
0. Consider(4)
E
E
L
=
∫
0
T
P
E
L
d
t
.The mathematical model of the F-IVT given above (see (1)–(4)) is implemented to estimate the performance of the F-IVT. In this work the F-IVT sizing was carried on in such a way that it is capable of powering the knee joint under different locomotion regimes, namely, the level ground walking at different speeds and the stairs climbing at different inclinations. In particular, the size of the HD gear and that of the motor were determined from the maximum power requested considering all possible walking regimes, whereas the most frequent one (level ground walking at 1.1 m/s) was used to optimally design the F-IVT in order to make it work very efficiently most of the time. More details about the criterion followed to size each component of the F-IVT, the nominal values of which are listed in Table 1, can be found in Appendix B.Table 1
Model parameters of the actuators F-IVT, SEA, and C-SEA. The motor damping parameters and the Coulomb friction torque are not provided by data sheet, but they were estimated following the guidelines given by Maxon.
F-IVT
SEA
C-SEA
Brushless motor
Model
EC-max 40283871
EC 60167131
EC 45136209
C
f
r [mNm]
5.2
0.8
0.77
J
M [g cm2]
101
831
209
k
e
m
f [V/rad/s]
0.0628
0.147
0.0739
k
t [mNm/A]
62.8
147
73.9
R [Ω]
2.02
1.03
1.01
ν [Nm/rad/s]
8.66
·
10
-
6
1.4
·
10
-
4
2.7
·
10
-
5
i
C
[A]
—
0.25
v
C
[V]
—
24
Flywheel
J
v [g cm2]
5
·
10
3
—
—
IVT
τ
I
V
T
[−1.35, 1.21]
—
—
Gear train
τ
G
T
1/50
1/80
1/143
η
G
T
By model
By model
0.9
Spring
K [Nm/rad]
—
375.14
250


## 2.2. Series Elastic Actuator (SEA)

SEAs have been extensively employed in wearable devices for lower limbs. In SEAs a spring is put in series between the motor and the artificial powered joint (Figure5(a)). The elastic element gives advantages to the actuation system such as increasing of shock tolerance and limited high frequency actuator impedance and energy storage [8–10]. Since the force/displacement characteristic of the spring is linear, the SEA is very efficient in powering the knee joint because it can be designed to take advantage of the linear torque-angle (or spring-like) relationship of the knee in the early stance flexion-extension phase of level ground walking. In particular if the stiffness of spring (K) is chosen equal to the slope of the torque-angle curve, the spring alone would render the spring-like relationship, resulting in a great reduction of the motor mechanical energy requirement.Figure 5
Schematic pictures of the SEA (a) and C-SEA (b).
(a)
SEA
(b)
C-SEAIn this work the electric power and energy requirement of SEA to power knee joint in level ground walking at different speeds and in stairs climbing at different inclinations are calculated through (3)-(4) as a function of angle (ϑ
M
=
C
K
/
K
+
ϑ
K
1
/
τ
G
T, τ
G
T being speed ratio of the gear train) and torque (C
M
=
C
K
τ
G
T
/
η
G
T, η
G
T being efficiency of the gear train) requirements of the SEA motor.As done for the F-IVT, the SEA was also sized to power the knee joint even under the most powerful condition examined and it was optimized according to the most frequent one. In particular the most powerful condition leads to the choice of both the motor and the HD, whereas the most frequent one leads to the choice of series stiffness which minimizes the energy consumption. In our calculations we used the same walking cycles of [17] so also the optimal value of the stiffness coefficient of the spring is the one determined in [17].According to [24], the gear train of the SEA comprises a harmonic drive gear (HD). The value of gear ratio of the HD is larger for SEA than for the F-IVT to reduce the maximum torque value requested to the motor and thus to limit the motor size. This choice leads to an average efficiency of the HD that is smaller than that in the F-IVT. The selected 400 W brushless Maxon Motor (model: EC 60 p.n. 167131) is able to provide the maximum torque requested to the motor (C
M
m
a
x
=
1.494 Nm) while working under the motor speed limit (ω
M
m
a
x
=
7322 rpm). We noticed that this motor is too heavy for a proficient use in a wearable device, but, on the other hand, it is the only one allowing the SEA to power the knee in all the conditions examined. The model parameters adopted are listed in Table 1.


## 2.3. Clutchable Series Elastic Actuator (C-SEA)

The C-SEA (Figure5(b)) was developed to overtake one limit of SEAs related to the inefficiency of the motor in the stance phase [7]. In fact, even if SEAs greatly reduce the motor mechanical energy requirement in the stance phase when the spring alone powers the knee joint, the electric motor works at very slow speeds and thus very inefficiently. The C-SEA improved the design of SEAs by including a clutch on the motor shaft that is conveniently activated or deactivated according to the cycle phase. In particular during the spring-like phase of the gait cycle the clutch is activated and the spring renders the complete torque-angle relationship while the motor is required to supply only reactionary torque; during the other phases of the cycle, the clutch is deactivated and the C-SEA works as a SEA.Similar equations as those of SEAs govern the operation of the C-SEA. The complete set of equations given in [7] follows:(5)
C
M
=
C
K
τ
G
T
η
G
T
clutch  off
0
clutch  on
,
ϑ
M
=
C
K
K
+
ϑ
K
1
τ
G
T
clutch  off
0
clutch  on
,
i
M
=
C
M
k
t
+
J
M
ω
˙
M
k
t
+
ν
ω
M
k
t
+
sign
⁡
ω
M
C
f
r
k
t
clutch  off
i
C
clutch  on
,
v
M
=
R
i
M
+
k
e
m
f
ω
M
clutch  off
v
C
clutch  on
,where i
C is the clutch current and v
C is the clutch voltage when the clutch is activated.In this work the authors estimated the electric energy and power consumption of the C-SEA in level ground walking at different speeds and in stairs climbing at different inclinations. The mathematical model and many of the parameters of [7] were adopted to calculate the performance of C-SEA. However, because of the different reference gait cycle data some characteristics have been changed and a bigger electric motor was selected. A 250 W brushless Maxon Motor (model: EC 45 p.n. 136209, parameters in Table 1) was chosen because it is able to provide a peak torque compatible with the maximum required (C
M
m
a
x
=
0.323 Nm) in the locomotion regime explored and the maximum motor speed (ω
M
m
a
x
=
11574 rpm) is always below the motor speed limit. The optimal spring stiffness value (K) was also not the same as [7] because of the different gait cycles data considered in this work. In particular, the optimal spring stiffness in [7] is defined as the one which minimizes the kinematic similarity defined as(6)
Ψ
=
∫
ϑ
C
S
E
A
-
ϑ
K
2
d
t
,where ϑ
C
S
E
A is the output displacement of the C-SEA and ϑ
K is the output displacement of the knee joint. Such criterion was adopted by Rouse et al. in [7] because they proved that the stiffness of the spring does not affect the electrical power profiles but determines very different knee kinematics. Indeed, when the stiffness affects the knee angle displacement, the clutch absorbs a nearly constant electrical power. Based on this minimization criterion, we calculated an optimal stiffness value of 250 Nm/rad, at which the kinematic agreement was of 8
·
10
-
4 rad2 s (Figure 6).Figure 6
Kinematic similarity (Ψ) as a function of series stiffness averaged across walking speeds for subject weight of 75 kg. The minimum value of Ψ is kept approximately at the series stiffness value of 250 Nm/rad.


## 3. Results and Discussion

The electric power and energy consumption of F-IVT, SEA, and C-SEA actuators were estimated through the models described in Section2, following an inverse dynamic approach. All the models parameters are listed in Table 1. Representative weight-normalized human locomotion data [17, 18] were given as input to the models to estimate the performance of all the actuators in powering the knee joint of a 75 kg person walking at different speeds and climbing stairs of different inclinations.The electric energy demanded by the motor and the electric power profile result from the simulations done. These quantities are significant performance indexes for the development of lightweight and portable wearable robots because they affect the size and the weight of the actuator, as well as the operating range of the device.The motor generation of electric energy has been usually neglected in the literature, because the efficiency of regeneration was considered to be too small. Only recently some researchers claimed that at the present state of the art the electric motors are enough efficient to permit a proficient use of the regenerative braking also in biomechatronic devices [7]. Indeed, although mathematical model of the brushless motor (Section 2.1) predicts very large values of the efficiency of the electric motor in the 2nd and 4th quadrant, experimental measurements are only in qualitative agreement with the model, since the measured values of efficiency are in the range 18–30% [25]. Therefore, two different estimations of the electric energy requirement were carried on in this work for SEA and C-SEA devices: in the first one the possibility of regenerating electric energy is considered; in the second one it is neglected. This distinction does not concern the F-IVT where the electric drive always works as a motor, providing a positive amount of energy in the whole gait cycle at all the walking speeds and at all the stairs inclinations.When the electric energy requirement of the F-IVT is compared with the electric energy requirements of SEA and C-SEA (Figure7) two cases must be distinguished: SEA and C-SEA with regenerative braking and with no regenerative braking. In the former case (Figures 7(a) and 7(b)) the F-IVT is the most power-demanding device at all the conditions of walking and stairs ascending. The C-SEA is the only one actuator with a total negative energy requirement at all the level ground walking speeds, and this is due to the greater efficiency of the transmission devices when compared to efficiencies of the SEA. In fact, even if the motor of SEA generates electric energy when the motor power is negative, as a consequence of the low value of η
H
D, which is often such to prevent the back drivability of the system, the total energy required by the motor is always positive for SEA.Figure 7
Motor electric energy requirement of the actuators compared (F-IVT, SEA, and C-SEA) in level ground walking at different speeds (a, c) and in stairs climbing at different inclinations (b, d), under the assumptions of regenerative braking admitted (a, b) and not admitted (c, d).
(a)
(b)
(c)
(d)In the no-regenerative braking case, the SEA has the greater electric energy consumption almost at all the walking speeds, whereas the C-SEA is still the most convenient one because of the low motor power absorbed when the clutch is activated (Figure7(c)).In stairs climbing the F-IVT always needs more electric energy than the SEA and the C-SEA if the regenerative braking of the motor is either considered or not (Figures7(b) and 7(d)), whereas the C-SEA proves to be the most advantageous solution. It can be noticed that there is no evident difference of the values of energy required by SEA and C-SEA in stairs climbing between the regenerative and the nonregenerative cases. In fact, while the total energy required by the knee in level ground walking is negative, it is positive in stairs climbing and thus the possibility of recovering energy is reduced.The peak of electric power is another important factor to estimate the performance of an actuator for lower limb joints, because it affects the size and the weight of the motor (Figure8). The F-IVT permits greatly reducing the electric peak power at all the locomotion conditions, if the regenerative braking of the motor is either considered or not. In fact one of the achievements of the F-IVT is to stabilize the working point of the motor, which provides a nearly constant amount of power whose value is close to the mean value of the power request and by far less than the peak (Figure 9). On the contrary, the motor of both the SEA and C-SEA has to follow the torque request of the knee joint, supplying variable power. This is clearly shown in Figure 9 where the instant value of motor power is shown as a function of time for all the devices under analysis and in two walking regimes, for instance, walking at 2.1 m/s (Figure 9(a)) and stairs climbing at inclination of 30° (Figure 8(b)). Similar results have been obtained in all other walking regimes.Figure 8
Electric peak power of the motors of the actuators compared (F-IVT, SEA, and C-SEA) in level ground walking at different speeds (a) and in stairs climbing at different inclinations (b).
(a)
(b)Figure 9
Instant power requirements of the knee joint and of the electric motor of the actuators compared (F-IVT, SEA, and C-SEA) in level ground walking at 2.1 m/s (a) and in stairs climbing at inclination of 30° (b).
(a)
(b)From these results the F-IVT seems to be the most effective solution for reducing the peak power of the motor, whereas the C-SEA is more energy efficient in all the conditions examined, if the regenerative braking is either permitted or not. On one hand, the F-IVT would permit a consistent electric motor downsizing; on the other hand, C-SEA would permit reducing the electric energy demanded by the motor for a given working range of the device. However, the gap between the C-SEA and the F-IVT in terms of energy consumption is considerably larger in the case of regenerative C-SEA, where our calculations may be affected by an overestimation of the electric energy recovered by regenerative braking with respect to the value achievable in practice [23].Furthermore, the power losses in all electric modules may also alter the comparison of energy consumption of F-IVT and C-SEA (or SEA), and they have not been considered in this study. Indeed, all electronic modules and also the batteries would work differently in the F-IVT and in C-SEA (or SEA): in one case the electric power is almost constant with constant angular velocity of the motor; in the other cases both the power and the velocity of the motor vary periodically. Therefore, the total energy consumption of the actuators, that is, the energy requirement of the battery, may be quite different from the electric energy demanded by the motor.


## 4. Conclusions

In this work the authors compared the motor performance of three different actuators, F-IVT, SEA, and C-SEA, powering an artificial knee joint under different locomotion regimes very recurring in daily life: level ground walking at different speeds and stairs climbing at different inclinations. Detailed efficiency models of all the devices were developed to obtain realistic estimations of the motor consumptions following an inverse dynamic approach.Two main performance indexes have been taken into consideration for comparison: the energy consumption (per gait) and the peak of electric power, both calculated at motor electrodes.As a result of the simulations, it was found that the motor of the C-SEA has an electric energy consumption which is always lower compared to the F-IVT and the SEA at all the locomotion regimes considered. Thus the C-SEA would permit a larger operating range of the device. However, it is important to specify that in this work the energy requirement of the motor has been calculated at the motor electrodes, not at batteries. There are at least two reasons why the effective energy requirement of the actuators, that is, the energy demanded by the battery, may be different with respect to the motor energy requirement, in particular in SEA and C-SEA. First, the working point of the motor is quickly and repeatedly variable, and this may affect the actual efficiency of the electronic devices between the batteries and the motor and the batteries themselves. Second, the electrical power generated by the motor could be smaller than the estimated, as the very low experimental values of the regeneration efficiency achieved in practice [23] would demonstrate. Unfortunately, these issues are still debated, and no precise data are available in the literature.Furthermore, in this study it was also proved that the F-IVT permit achieving a drastic reduction of the peak power at all the conditions examined. In fact, the flywheel and the IVT stabilize the working point of the motor, which always provides a nearly constant amount of power that is very lower than the peak power request. This achievement is very important in view of the possibility of downsizing the electric motor, which would also mean reducing the size and the weight of the actuator, with advantages in terms of portability. Of course, even if the motor mass is the most critical one, in order to make the F-IVT more lightweight than the other devices developed for the same purpose, the mass loss due mainly to the reduced motor size should overcome the additional masses of the micro-IVT and the flywheel.Moreover, the motor of the F-IVT always works very efficiently, even when it does not work under the condition for which it is optimized, and this may be true for the power electronics and the batteries.The comparison of the three actuators done in this paper aims at evaluating which are the potential benefits or the drawbacks of the F-IVT actuator, in order to evaluate if it could or could not be a competitive actuator for artificial knee joints of wearable robots. Furthermore, the results of the comparison are usefully supporting the development of a prototype of the F-IVT in which the authors are involved. For example, a careful analysis of the results obtained in this work reveals that at the present state of the art the weak point of the F-IVT is the overall efficiency of the driveline, the bottleneck of which is the harmonic drive. These results stimulate to find alternative possibilities in order to improve the efficiency of F-IVT to reduce the motor energy requirement, keeping its indisputable advantages safe.



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*Source: 4802474-2016-03-16.xml*