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Technical Brief

Design and Testing of an Innovative Wire Transmission for a Quarter-Turn Actuator

[+] Author and Article Information
L. Pugi, E. Galardi

Department of Industrial Engineering,
University of Florence,
Florence 50139, Italy

N. Lucchesi

VELAN ABV, S.p.A.,
Capannori (LU),
Lucca 55012, Italy

Manuscript received March 30, 2015; final manuscript received December 17, 2015; published online March 7, 2016. Assoc. Editor: Xianmin Zhang.

J. Mechanisms Robotics 8(4), 044501 (Mar 07, 2016) (11 pages) Paper No: JMR-15-1078; doi: 10.1115/1.4032404 History: Received March 30, 2015; Revised December 17, 2015

The object of this work is the development of an innovative wire actuator in collaboration with Velan ABV S.p.A., which will be mainly used in applications in which high efficiency and linear behavior are desirable specifications. In this work, the main features of the proposed actuator, which is protected by a patent, are evaluated and compared with respect to a conventional solution consisting of a scotch yoke (SY) transmission system. The comparison is performed using both the simulation results and the experimental data. In order to identify the efficiency and the dynamical response of the innovative actuator, the authors have designed a hydraulic test rig, which can be configured to perform different testing procedures. In this way, it is possible to perform both static tests to identify actuator efficiency, and dynamic ones, in which an assigned load or a valve impedance function is simulated to verify the response of the tested actuator in realistic conditions. Finally, the proposed test rig has been successfully employed to perform both reliability and fatigue tests in which the actuator is subjected to realistic and repetitive loads.

Copyright © 2016 by ASME
Topics: Actuators , Valves , Design
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References

Figures

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Fig. 1

Example of a quarter-turn valve actuation system using a pneumatic cylinder and a SY transmission system

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Fig. 2

Simplified static scheme of the SY actuator. (a) Simplified kinematic scheme and notation; exchanged forces (neglecting inertial forces) during opening (b) and closing (c) maneuvers of the actuator.

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Fig. 3

Simplified static models of the proposed actuator in the parallel (a) and in the aligned (b) configurations during the opening phase

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Fig. 5

LMSAmesim model of the SY actuator

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Fig. 6

Comparison of efficiency calculation between LMS Amesim model of the SY and corresponding calculation using the relation (2)

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Fig. 7

LMS Amesim model of the innovative actuator (β = 90 deg)

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Fig. 8

Efficiency η calculated as a function of θ and β assuming a constant ρ* equal to 3 mm

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Fig. 9

Solution with β equal to 14 deg

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Fig. 10

Comparison between the innovative actuator and the SY one

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Fig. 12

Main components of the test rig

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Fig. 14

Behavior of the transmission ratio of the test rig in respect to its value on the lower end-run τ(0)

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Fig. 15

Measured and calculated torques in opening and closing run in respect to the opening percentage (100% = 90 deg)

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Fig. 16

Measured torque values with the innovative actuator compared with the corresponding ideal one (no losses) and the theoretical ones calculated according to Eq. (7) and considering a constant equivalent friction radius ρ of 3 mm

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Fig. 17

Measured efficiency of the SY and innovative (P&C) actuators in the opening and in the closing run respect to theopening percentage (100% = 90 deg) and respect to the calculated efficiency

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Fig. 18

Typical torque profiles needed to open and to close a ball valve

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Fig. 19

Error on the simulated torque of the rig considering a constant reference value of 600 and 1200 N·m and a feeding pressure of the pulley actuator of 6.5 bar G

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Fig. 20

Measured position of the pulley actuator with a constant pressure of 6.5 bar G and a constant simulated load of about 600 or 1200 N·m

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Fig. 21

Measured velocity of the pulley actuator with a constant pressure of 6.5 bar G and a constant simulated load of about 600 or 1200 N·m

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Fig. 22

Repeatability of reliability tests comparison of the response for the first four-load cycles

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Fig. 23

Layout of the test rig with the innovative actuator

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