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ORIGINAL ARTICLE
Design and Analysis of an Active Helical Drive Downhole Tractor
Yujia LI1 • Qingyou LIU2• Yonghua CHEN3
• Tao REN1
Received: 18 January 2016 / Revised: 11 May 2016 / Accepted: 22 August 2016 / Published online: 16 March 2017
� Chinese Mechanical Engineering Society and Springer-Verlag Berlin Heidelberg 2017
Abstract During oil-gas well drilling and completion,
downhole tools and apparatus should be conveyed to the
destination to complete a series of downhole works.
Downhole tractors have been used to convey tools in
complex wellbores, however a very large tractive force is
needed to carry more downhole tools to accomplish works
with high efficiency. A novel serial active helical drive
downhole tractor which has significantly improved per-
formance compared with previous work is proposed. All
previously reported helical drive downhole tractors need
stators to balance the torque generated by the rotator. By
contrast, the proposed serial downhole tractor does not
need a stator; several rotator-driven units should only be
connected to one another to achieve a tractive force mul-
tifold higher than that was previously reported. As a result,
the length of a single unit is shortened, and the motion
flexibility of the downhole tractor is increased. The major
performance indicators, namely, gear ratio, velocity, and
tractive force, are analyzed. Experimental results show that
the maximum tractive force of a single-unit prototype with
a length of 900 mm is 165.3 kg or 1620 N. The analysis
and experimental results show that the proposed design has
considerable potential for downhole works.
Keywords Serial � Active � Helical � Downhole � Tractor �Wellbore
1 Introduction
Unconventional or low-permeability oil and gas produc-
tivity can be greatly enhanced by drilling horizontal,
deviated, and extended-reach wells [1–3]. During well
drilling and completion, downhole tools and apparatus used
for well logging, workover, flushing, fishing, and perfo-
rating should be conveyed to the destination. The tradi-
tional downhole conveyance technology is not applicable
to these complex wellbores [4]. In response to the chal-
lenges presented by complex well trajectories, downhole
tractors have been used since the 1990s to convey evalu-
ation, remediation, and intervention tools [5]. Using
downhole tractors costs less because they do not necessi-
tate the use of drilling rigs. In addition, downhole tractors
can be positioned precisely to conduct cutting and perfo-
rating. Fig. 1 shows the principle of a downhole tractor
operating in an oil or gas well.
Various in-pipe robot topologies have been developed
since the 1950s [6]. They can be classified into eight dif-
ferent types according to their driving mechanisms [7–13],
i.e., pig, wheeled, caterpillar, wall press, walking, inch-
worm, helical, and snake. These types of in-pipe robots
have their own advantages in specific working spaces and
environments. In the 1970s, the high maintenance
requirements of the pipeline, tank container, and wellbore
used in harsh environments, such as oil, natural gas, shale
gas, and nuclear industry, spurred the development of in-
Supported by Sichuan Provincial Science and Technology Program of
China (Grant Nos. 2013GZ0150, 2014GZ0121), and Research Project
of Key Laboratory of Fluid and Power Machinery of Ministry of
Education, Xihua University, China.
& Qingyou LIU
1 School of Mechatronic Engineering, Southwest Petroleum
University, Chengdu 610500, China
2 Key Laboratory of Fluid and Power Machinery of Ministry of
Education, Xihua University, Chengdu 610039, China
3 Department of Mechanical Engineering, The University of
Hong Kong, Hong Kong, China
123
Chin. J. Mech. Eng. (2017) 30:428–437
DOI 10.1007/s10033-017-0076-6
pipe robots. Owing to the special functional and environ-
mental restrictive conditions, namely, high pressure, high
temperature, strong corrosion, small diameter, and large
payloads in wellbores, only two of the aforementioned
types of in-pipe driving mechanisms are used in downhole
tractors, namely, wheel-type continuous driving and inch-
worm reciprocating driving [4].
In 1993, Statoil and Welltec became the first companies
to research on cable-driven downhole tractor based on
wheel-type continuous driving. Their product consists of a
motor, hydraulic system, driving wheel unit, controlling
unit, and pressure compensation system [14]. The motor
drives hydraulic pumps to generate a certain pressure force
and friction force. GE Oil and Gas Company developed a
downhole tractor driven by only motors and mechanical
transmissions [15]. With a body length of 7.46 m, it could
log while tractoring and accommodate payloads of up to
2675 N. Aker Solutions also devised a wheel-driven
downhole tractor, which has a pulling force of 2225 N per
drive section and a capability for open-hole logging. This
type of downhole tractor can work in small wellbores.
However, it cannot be used for high payloads and large
wellbores.
Another widely used downhole tractor is of the inch-
worm reciprocating driving type. Reciprocating driving
uses locking devices and imitates the motion of an inch-
worm with an anchor–extend–release–re-anchor movement
[4]. Smart Completions Ltd. has designed an electro-hy-
draulic fully bi-directional crawler-type tractor named
SmarTract Robotic Downhole Tractor [16], which is 10 m
long and has a maximum pulling force of 6664 N and a
speed of up to 549 m/h. Omega Completion Technology
and WWT have also developed downhole tractors of this
kind [17]. Their tractors have both high speed and large
pushing or pulling force. Moreover, their downhole tractors
are applicable to a wide range of pipe diameters. Never-
theless, their motion is discontinuous; thus, they cannot
perform logging and tractoring simultaneously.
In recent years, many studies have focused on helical in-
pipe robots, which are driven by only one motor and have a
simple structure and control system [18–23]. Although
these typical helical in-pipe robots possess increased
motion stability, to our knowledge, they are all passively
driven, that is, the driving wheel rotates passively relying
on the friction force exerted by the pipe wall on the wheels.
As a result, the mechanical transmission efficiency of these
in-pipe robots is low, and their tractive force is insufficient
for drag testing or repairing downhole tools. Accordingly,
we proposed in our previous work [24] a novel active
helical drive in-pipe robot with a compound planetary gear
system to increase traction significantly. However, this
helical drive in-pipe robot is composed of at least two
units, namely, a rotator and a stator, according to the laws
of action and reaction [25]. This traditional type of helical
drive structure increases the length of the robot and con-
sequently reduces its motion flexibility.
To realize a larger payload, better motion flexibility, and
simultaneous logging and tractoring, we propose a novel
active helical drive downhole tractor with a serial structure.
Unlike traditional helical in-pipe robots, this novel down-
hole tractor does not require a stator to balance the torque
generated by the rotator. Several rotator-driven units only
need to be connected to one another to obtain a tractive
force multifold higher than those of previous in-pipe
robots.
2 Concept and Design of the Serial Active HelicalDrive Downhole Tractor
2.1 Overview on the Structure
Fig. 2 shows two different structures of active helical-drive
downhole tractors. Fig. 2(a) shows the traditional structure,
which consists of a rotator and a stator. The driving motor
is installed on the stator and provides the driving force to
the tractor. The centering wheels installed on the stators
play a significant role in centering and guiding. The driving
wheels and wellbore comprise a compound planetary gear
system, in which the sun gear is driven directly by the
motor. As the rotator, the driving wheels, are in contact
with the wellbore and produce a forward driving force. In
this configuration, the stator is an indispensable part to
balance the torque generated by the rotator.
Fig. 2(b) shows a novel serial structure with rotators only.
The driving motor is installed on the rotator and rotates
together with the planet carrier. Owing to this significant
improvement, a stator is no longer needed to balance the
Fig. 1 Principle of a downhole tractor operating in an oil or gas well
Design and Analysis of an Active Helical Drive Downhole Tractor 429
123
torque; thus, the length of a single unit can be shortened,
and a more flexible motion can be realized. The driving
wheels can be used not only as a driving unit but also as a
centering unit. Thus, the tractor can be centered inside the
wellbore, and the motion stability of the downhole tractor
can be consequently enhanced. This tractor can perform
logging while tractoring.
2.2 Structural Design of a Single Driving Unit
Fig. 3 shows the structure of the proposed downhole trac-
tor. It consists of a motor, controlling PCB, planetary gear
system, and other transmission mechanisms. Motor 1 is the
motor driving the sun gear directly. The sun gear is in mesh
with the first planetary gear set. The second planetary gear
set is connected to the first planetary gear set by three
telescopic universal joints. Motor 2 is used to drive the ball
screw, which is connected to the linear slider, and to push
or pull the connecting rod by moving in the axial direction
so as to auto-control the contraction and expansion of the
driving wheels. The moving direction is marked by arrows
in Fig. 3. A spring is used to allow the downhole tractor to
adapt to small changes in pipe diameters and prevent the
deflection of the tractor from the wellbore because of
impurities or the localized deformation in the pipeline. The
driving wheels press firmly onto the internal wall of the
wellbore and tilt at an angle when in operation. The pipe
wall is engaged as the internal ring gear of the planetary
gear system. Then, a tractive force is generated. Motor 1 is
fixed on the body of the tractor and rotates together with
the planet carrier. Therefore, all the forces generated are
the internal forces of the compound planetary gear system.
A stator is unnecessary to balance any external torque.
3 Gear Ratio, Velocity, and Force Analysis
3.1 Description and Definition of Helical Angle
Figs. 4(a), (b), and (c) show the driving unit viewed from the
front, right, and top, respectively. Three important angles,
i.e., a, c, and u, are defined and shown in Fig. 4. Angle a is
the helical angle of the driving wheels, that is, the angle
between the following two geometric features [24]:
(1) The intersecting line between the wheel plane and
the plane tangent to the circumference of the pipe
wall at the contact point of the wheel and the pipe
wall;
(2) The pipe cross-section through the contact point of
the wheel and the pipe wall.
The helical angle can be calculated as follows [26]:
tan a ¼ tan c sinu: ð1Þ
3.2 Gear Ratio and Velocity
Gear ratio is the most important factor in a compound
planetary gear system as it decides the relationship between
the parameters of the driving motor and the moving speed
of the tractor. Fig. 5 shows the kinematic diagram of the
gear transmission with serial two-unit structure. The body
Fig. 2 Two different structures of active helical drive in-pipe robots
1st Planetary gear set
2nd Planetary gear set
Telescopic universal joint Connecting rod
Ball screw
Embedded springBody(motor1 and controlling PCB)
Motor 2
Linear slider
Planetary carrier
Fig. 3 Structural design of serial active helical drive downhole
tractor (single unit)
430 Yujia LI et al.
123
of the driving motor rotates together with the planetary
carrier. Fig. 6 presents the simplified gear transmission
diagram of the single driving unit. Symbols S, H, 1, 2, and
P in Fig. 6 represent the sun gear(connected to the output
shaft of the motor), the planetary carrier, first planetary
gear set, second planetary gear set, and pipe wall, respec-
tively. The pipe wall can be regarded as the internal ring
gear of the compound planetary gear system. Thus, the
angular velocity of the pipe wall is zero. The gear ratio iHsPbetween the sun gear and the pipe wall (internal ring gear)
can be calculated by
iHsP ¼ xs � xH
0� xH
¼ 1� isH; ð2Þ
where xs and xH are the absolute angular velocities of the
sun gear and planetary carrier relative to the pipe, respec-
tively. Thus, the gear ratio isH between the sun gear and
planetary carrier is
isH ¼ 1� � z1zP
zsz2
� �; ð3Þ
where z1, z2, zs, and zP are the numbers of the respective
gear teeth. In this study, the diameter of the pipe, DP,
should replace zP. Parameter z2 should be replaced with the
pitch diameter of the driving wheel, D2. Thus,
isH ¼ 1þ z1DP
zsD2
¼ xs
xH
: ð4Þ
If z1 = 30, zs = 20, DP = 105 mm, and D2 = 36 mm,
then the gear ratio between the sun gear and the planetary
carrier is 5.375. Thus, we can obtain the relative angular
velocity between the sun gear and the motor body (planetary
carrier) based on the basic parameter of the driving motor.
xs � xH ¼ isH � 1ð ÞxH ¼ 2pn60
; ð5Þ
where n is the rotation speed of the driving motor. If the
rotation speed is known, then the absolute angular velocity
of the planetary carrier can be obtained.
Finally, the relationship between the moving speed, v, of
the tractor and xH can be established as follows:
v ¼ xH � rP � tan a; ð6Þ
where rP is the radius of the pipe. If the rotation speed is
the rated speed of 170 r/min and the helical angle, a, is themaximum value of 18�, then the moving speed is
69.38 mm/s.
3.3 Force Analysis
3.3.1 Driving Force Analysis
Analyzing the driving force of the downhole tractor is of
significance because the driving force affects the mechan-
ical structure design and real application scope [27]. The
force diagram of a driving wheel is shown in Fig. 7.
(a) Front view (b) Right view
(c) Top view
φ
γ
α
Fig. 4 Definition of angles a, c, and u
Fig. 5 Kinematic diagram of the gear transmission
Fig. 6 Simplified gear transmission diagram of the single driving
unit
Design and Analysis of an Active Helical Drive Downhole Tractor 431
123
Three forces act on the wheel to ensure its steady state
of motion. The equilibrium equations for the forces acting
on the driving wheel are as follows:
FT �W � sin a ¼ 0;Ff �W � cos a ¼ 0;
�ð7Þ
where W is the pulling force exerted by the load on each
wheel, Ff is the sliding friction force exerted by the internal
pipe wall on the driving wheel, and FT represents the tor-
que of the driving wheel. If the rated rotation speed, n, and
rated power, P, of the motor are known, then the rated
torque can be calculated. Thus, FT can be obtained as
follows:
FT ¼ 9550P � is2
3n � D2/2; ð8Þ
where is2 is defined as the gear ratio between the sun gear
and the second planetary gear set and is related to the pipe.
Given that the first and second planetary gear sets have the
same angular velocity, is2 can be replaced with is1. The gear
ratio between the sun gear and the first planetary gear set in
relation to the carrier is as follows:
iHs1¼ xs � xH
x1 � xH
¼ � z1
zs: ð9Þ
The angular velocity, x1, of the first planetary gear set
can be obtained by substituting Eqs. (2), (4), and (5) into
Eq. (9). Subsequently, the gear ratio is2 can be calculated
as follows:
is2 ¼xs
x1
: ð10Þ
The maximum pulling force of the entire tractor can be
obtained by substitute Eqs. (8) and (10) into Eq. (7). Fig. 8
shows the relationship between a, P, and 3 W.
3W ¼ 3FT
sin a¼ 19 100P z1DP þ zsD2ð Þ
nD2 sin a zsD2 � zsDPð Þ : ð11Þ
3.3.2 Torque-Balance Analysis
A torque-balance analysis is conducted to compare the
novel serial active helical drive structure with the tradi-
tional one. As shown in Fig. 9(a), the motor body, which is
connected to the centering wheels, is the stator. The planet
carrier is used as a rotator, and it rotates in relation to the
stator. When the gears are in mesh and rotate, the sun gear
is subjected to an anti-torque. The motor body bears the
anti-torque. Given that the motor body and the centering
wheels are connected, the pipe exerts a torque to balance
the anti-torque.
By contrast, in the novel serial active helical drive
structure (Fig. 9(b)), the motor body is the rotator. It rotates
together with the planetary carrier. Different from the tra-
ditional structure, the planetary carrier and motor body in
the novel structure bear the anti-torque. Thus, the outside
environment should not provide a torque, and a stator is not
necessary in this structure. This design simplifies the
structure, enhances motion flexibility, and improves the
strength of the parts.
4 Experiments
4.1 Prototype
A prototype based on the design in Fig. 10(a) is con-
structed, as shown in Fig. 10(b). The outer diameter of the
tractor body is 74 mm. The length of the entire body of the
tractor is 900 mm. DC Motor 1 (200 W, 170 r/min) is used
to provide power to the entire tractor system. DC Motor 2
can auto-control the contraction and expansion of the
driving wheels.
The centering unit, also called testing unit, is fabricated
to test the tractive force of a single tractor, as shown in
Fig. 11. Each wheel arm is equipped with a force sensor.
When the centering unit is placed into the pipe, the
pressing force between the centering wheels and internal
pipe wall can be monitored and adaptively adjusted
automatically.
FfFT
Wα
Fig. 7 Force diagram of a driving wheel
Fig. 8 Relationship between a, P, and 3 W
432 Yujia LI et al.
123
4.2 Control System
As shown in Fig. 12, the downhole tractor is driven by two
DC motors, which are equipped with encoders. An MCU
controls the driving module via the PWM; thus, the current
of the motors can be controlled. A DC power supply pro-
vides power to the driving module and MCU. At the same
time, the MCU communicates with other modules by using
RF (Radio Frequency) technology. Owing to the short
transmission distance of an RF signal in metal pipelines, a
special design is proposed. The RF signal is coupled to a
DC power supply through the capacitor to form a system
similar to a power line carrier system. Using this structure,
we only need to connect the multiple downhole tractors and
control them altogether.
We also develop a software to control the downhole
tractor by computers. Fig. 13 shows the interface and
function of this control software. The contraction and
expansion of the driving and centering wheels can be
controlled to enable the wheels to press onto the internal
wall of wellbore firmly. The rotation speed can be changed
by dragging the speed adjustment bar. The force of each
testing arm and the current of the driving motor are dis-
played on this software interface. The values of the tractive
force can be collected by the force sensor and shown on the
computers.
Fig. 9 Torque-balance comparison of two active helical drive
structures
(a) Design model
(b) Prototype of two driving units
1st Planetary gear set
2nd Planetary gear set
Body ( Motor 1 andControlling PCB )
Motor 2Ball screwLinear slider
1st Planetary gear set2nd Planetary gear set
Controlling PCB
Motor 2Ball screwLinear slider
Body
Motor
1
Fig. 10 Design and prototyping of the proposed tractor
Centering wheel
Motor 2
Linear slider and ball screw
Spring
Force sensor
Fig. 11 Prototype of the centering unit
Design and Analysis of an Active Helical Drive Downhole Tractor 433
123
4.3 Experimental Scenario and Results
A seamless steel tube with an outer diameter of 127 mm
and a length of 9 m is used in the experiment.
Fig. 14(a) presents a diagram of the experimental design.
The downhole tractor is placed into a seamless steel tube.
A power line communication system is used to provide
power to the tractor and communicate with the computers
at the same time. A hoisting cable, which passes through
two fixed pulleys, is tied to the tractor and connected to the
force sensor at the other end. An air cylinder and piston are
used for tightening the hoisting cable. When the tractor
moves forward, a tractive force acts on the force sensor,
and the instrument displays this tractive force.
Fig. 14(b) shows the actual experimental environment and
devices.
We gradually increase the air pressure in the air cylinder
when the tractor is moving forward in the pipe. As the
pressure and hoisting cable tension increase, the pulling
force acting on the tractor increases gradually. When the
driving wheels of the tractor skid and can no longer move
forward, the pulling force becomes the maximum tractive
force displayed on the instrument and recorded on the
computers. In the experiment, we continuously recorded
the tractive force for 53 s. Finally, the maximum tractive
force of the downhole tractor is 165.3 kg or 1620 N, as
shown in Fig. 15. This tractive force is much larger than
the 490 N tractive force of the active helical drive in-pipe
robot in our previous work [24]. Furthermore, the novel
single-unit downhole tractor is much shorter than the
existing original downhole tractors. However, its tractive
force per unit length is much larger than the original ones.
The driving voltage is 64 V in the experiment. The
current value of the driving motor is collected and shown in
Fig. 16, which shows that the current slightly fluctuates.
The possible reasons for the current fluctuation are as
follows:
Fig. 12 Structure of the downhole tractor control system
Fig. 13 Interface of the downhole tractor control software
(a) Schematic of the experiment
(b) Actual experimental environment and devices
Air cylinder
Traction display
Tractor in pipe
Power
Air bottle
Camara
Power
Air cylinderForce sensor
Traction display
Downhole tractor
PulleyPulley
Pipe
Fig. 14 Experimental environment and devices
434 Yujia LI et al.
123
(1) The center of gravity of the tractor leads to different
compression or elongation magnitudes of the three
driving arms. The deviation in manufacturing the
downhole tractor results in an asymmetric size.
These factors lead to pipe eccentricity and conse-
quently produce current fluctuation.
(2) The localized deformation and impurity accumula-
tion in the pipeline result in the driving wheels
skidding in relation to the pipe wall. As a result, the
current instantaneously decreases.
(3) The periodic revolution of the planetary gear system
causes small-scale fluctuations in the current of the
driving motor.
In the experiment, the average current is 2.5 A, and the
voltage is 64 V; thus, the power is 160 W. The rotation
speed of Motor 1 is 170 r/min. The helical angle of the
driving wheels is 15�. The teeth numbers of the sun gear,
first planetary gear set, and second planetary gear set are
20, 30, and 50, respectively. The inner diameter of the pipe
and the pitch diameter of the second planetary gear set are
105 mm and 36 mm, respectively. The maximum pulling
force (also called tractive force) of the tractor, which can
be calculated by Eq. (11), is 5413.18 N. The experimental
tractive force is 1620 N. The efficiency of the entire system
is approximately 30%.
The efficiency of the motor is approximately 86%, and
the transmission efficiency of the planetary gear reducer on
the motor is 65% [28]. The transmission efficiency of the
planetary gear is approximately 90%, and the transmission
efficiency of the two-stage planetary gear system is 81%.
Thus, the total efficiency of the entire system is 45.3%. In
addition, circuit and friction losses contribute to efficiency
reduction. The final estimated efficiency is approximate to
the calculated value. Therefore, the given theoretical
analysis is accurate.
5 Discussion
However, the design of the downhole tractor may be fur-
ther optimized. Given that the serial driving units are
rigidly connected, a push-and-pull effect will be generated
in case a power loss occurs. Another serious problem is the
possibility of the tractor being stuck in the pipe. A possible
solution to this problem is to replace the telescopic cross
shaft universal joint with a telescopic constant-velocity
universal joint to realize a constant-velocity transmission
between the driving shaft and the driven shaft. A telescopic
connection can compensate for the processing and assem-
bly errors. In addition, an overrunning clutch can be
installed on either side of the universal joint shaft. When
deformation and impurities exist in the wellbore, this
structure can protect the driving wheels from motion
interference and improve transmission efficiency. Further-
more, a flexible connection can be considered between
every two driving units to eliminate motion interference.
All the aforementioned possible solutions will be consid-
ered in our future work.
6 Conclusions
(1) A serial active helical drive downhole tractor is
proposed and prototyped. Unlike traditional helical
in-pipe robots, this novel downhole tractor does not
require a stator to balance the torque generated by
the rotator. Several rotator-driven units only need to
be connected to one another to obtain a tractive force
multifold higher than those of previous in-pipe
robots. Additionally, the length of a single unit can
be shortened, and a more flexible motion can be
realized.
(2) The driving wheels can be used not only as a driving
unit but also as a centering unit. Thus, the tractor can
be centered inside the wellbore, and the motion
stability of the downhole tractor can be consequently
enhanced. This tractor can perform logging while
tractoring.
(3) The gear ratio of the downhole tractor system is
calculated, and the velocity and force are analyzed.
Fig. 15 Tractive force recorded continuously
Fig. 16 Current fluctuation graph
Design and Analysis of an Active Helical Drive Downhole Tractor 435
123
Experiments are conducted to evaluate the tractive
force. The final estimated efficiency is approximate
to the calculated value. Therefore, the given theo-
retical analysis is accurate.
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Yujia LI, born in 1990, is currently a PhD candidate at School of
Mechatronic Engineering, Southwest Petroleum University, China.
She received her bachelor degree from Southwest Petroleum Univer-
sity, China, in 2012. Her research interests include the oil and gas
equipment, in-pipe inspection robot and the downhole tractor. E-mail:
Qingyou LIU, born in 1965, is currently a professor at Xihua
University, China. He received his PhD degree from Southwest
Petroleum University, China, in 1997. His research interests include
the oil and gas equipment, oil and gas wells engineering mechanics
and in-pipe inspection robot. E-mail: [email protected].
436 Yujia LI et al.
123
Yonghua CHEN, born in 1963, is currently a professor at University
of Hong Kong, China. He received his PhD degree from University
of Liverpool, England, in 1990. His research interests include
engineering design, rapid prototyping and robotic machining, haptic
modeling and computer aided medical surgeries. E-mail:
Tao REN, born in 1988, is currently a PhD candidate at School of
Mechatronic Engineering, Southwest Petroleum University, China.
He received his bachelor degree and master degree from Southwest
Petroleum University, China, in 2011 and 2014, respectively. His
research interests include the oil and gas in-pipe inspection robot and
the downhole tractor. E-mail: [email protected]
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