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TECHNICAL PAPERS

The Influence of Pulley Deformations on the Shifting Mechanism of Metal Belt CVT

[+] Author and Article Information
G. Carbone, L. Mangialardi, G. Mantriota

Dipartimento di Ingegneria Meccanica e Gestionale Politecnico di Bari V. le Japigia 182, 70126 Bari, Italy

J. Mech. Des 127(1), 103-113 (Mar 02, 2005) (11 pages) doi:10.1115/1.1825443 History: Received August 28, 2003; Revised April 27, 2004; Online March 02, 2005
Copyright © 2005 by ASME
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References

Gerbert, B. G., 1972, “Force and Slip Behavior in V-belt Drives,” Acta Polytechnica Scandinavica, Mechanical Engineering Series No. 67, Helsinki.
Gerbert, B. G., 1984, “Metal V-Belt Mechanics,” ASME paper, 84-DET-227.
Gerbert,  B. G., and Sorge,  F., 2002, “Full sliding adhesive-like contact of V-belts,” ASME J. Mech. Des., 124(4), pp. 706–712.
Carbone,  G., Mangialardi,  L., and Mantriota,  G., 2002, “Fuel Consumption of a Mid Class Vehicle with Infinitely Variable Transmission,” SAE J. Engines, 110(3), pp. 2474–2483.
Brace, C., Deacon, M., Vaughan, N. D., Horrocks, R. W., and Burrows, C. R., 1999, “The Compromise in Reducing Exhaust Emissions and Fuel Consumption from a Diesel CVT Powertrain over Typical Usage Cycles,” Proc. CVT’99 Congress, Eindhoven, The Netherlands, pp. 27–33.
Mangialardi,  L., and Mantriota,  G., 1999, “Power Flows and Efficiency in Infinitely Variable Transmissions,” Mech. Mach. Theory, 34, pp. 973–994.
Mantriota,  G., 2001, “Power Split CVT Systems with High Efficiency,” Proc. Inst. Mech. Eng., Part D (J. Automob. Eng.), 215(D3), pp. 357–368.
Carbone,  G., Mangialardi,  L., Mantriota,  G., and Soria,  L., 2004, “Performance of a City Bus equipped with a Toroidal Traction Drive,” IASME Trans., 1(1), pp. 16–23.
Gillespie,  R. B., Moore,  C. A., Peshkin,  M., and Colgate,  J. E., 2002, “Kinematic creep in a continuously variable transmission: Traction drive mechanics for cobots,” ASME J. Mech. Des., 124(4), pp. 713–722.
Kim,  J., Park,  F. C., Park,  Y., and Shizuo,  M., 2002, “Design and analysis of a spherical continuously variable transmission” ASME J. Mech. Des., 124(1), pp. 21–29.
Ide, T., Uchiyama, H., and Kataoka, R., 1996, “Experimental Investigation on Shift Speed Characteristics of a Metal V-Belt CVT,” JSAE paper 9636330.
Ide,  T., Udagawa,  A., and Kataoka,  R., 1995, “Simulation Approach to the Effect of the Ratio Changing Speed of a Metal V-Belt CVT on the Vehicle Response,” Veh. Syst. Dyn., 24, pp. 377–388.
Carbone,  G., Mangialardi,  L., and Mantriota,  G., 2001, “Theoretical Model of Metal V-Belt Drives During Rapid Ratio Changing,” ASME J. Mech. Des., 123, pp. 111–117.
Carbone,  G., Mangialardi,  L., and Mantriota,  G., 2002, “Influence of Clearance Between Plates in Metal Pushing V-Belt Dynamics,” ASME J. Mech. Des., 124, pp. 543–557.
Carbone, G., Mangialardi, L., and Mantriota, G., 2001, “Shifting Dynamics of Metal Pushing V-Belt—Rapid Speed Ratio Variations,” Integrated Powertrains and their Control, Professional Engineering Publishing (IMechE), Chap. 5.
Carbone,  G., Mangialardi,  L., and Mantriota,  G., 2003, “EHL Visco-plastic Friction Model in CVT Shifting Behavior,” Int. J. Veh. Des., 32(3–4), pp. 332–357.
Srnik, J., and Pfeiffer, F., 1997, “Dynamics of CVT Chain Drives: Mechanical Model and Verification,” Proc. of the 1997 ASME Design Engineering Technical Conferences, DETC97/VIB-4127.
Srnik,  J., and Pfeiffer,  F., 1999, “Dynamics of CVT chain drives,” Int. J. Veh. Des., 22, pp. 54–72.
Sattler, H., 1999, “Efficiency of Metal Chain and V-Belt CVT,” Proc. CVT’99 Congress, Eindhoven, The Netherlands, pp. 99–104.

Figures

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The kinematical and geometric quantities involved: (a) planar view; (b) 3D view
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The position of the belt material element at two infinitely close time instants
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The forces acting on the belt
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The sliding angle γ=ψ−π/2 of a chain link (drive pulley αI,drivingDR+π/2): (a) Srnik and Pfeiffer 17 (flexible sheaves: - - -, rigid sheaves: ———), (b) prediction of the model here presented. The extension of contact arc is α=180 deg and β0=10 deg.
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The sliding angle γ=ψ−π/2 of a chain link (driven pulley αI,drivenDN−π/2): (a) Srnik and Pfeiffer 17 (flexible sheaves: - - -, rigid sheaves: ———), (b) prediction of the model here presented. The extension of contact arc is α=180 deg and β0=10 deg.
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The tensile forces during one revolution: (a) Srnik and Pfeiffer 17, (b) prediction of the model here presented (the extension of contact arc is α=180 deg and β0=10 deg on both the pulleys, the friction coefficient is μ=0.1, the minimum tension of the belt is Fmin=1.6 kN and the ratio Fmin/Fmax=0.35).
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The normal forces in a chain link during one revolution: (a) Srnik and Pfeiffer 17, (b) prediction of the model here presented. (The extension of contact arc is α=180 deg and β0=10 deg on both the pulleys, the friction coefficient is μ=0.1, the minimum tension of the belt is Fmin=1.6 kN and the ratio Fmin/Fmax=0.35).
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The dimensionless parameter δ versus force ratio ξ for different values of A (the extension of contact arc is α=180 deg, β0=10 deg and the friction coefficient is μ=0.1).
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The dimensionless parameter δ versus ln(ξ) for different values of A (the extension of contact arc is α=180 deg, β0=10 deg and the friction coefficient is μ=0.1).
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The traction coefficient λ versus force ratio ξ for different values of A (the extension of contact arc is α=180 deg, β0=10 deg and the friction coefficient is μ=0.1).
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The traction coefficient λ versus ln(ξ) for different values of A (the extension of contact arc is α=180 deg, β0=10 deg and the friction coefficient is μ=0.1).
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the dimensionless parameter ADR as function of ln(SDR/SDN) (the extension of contact arc is α=180 deg, β0=10 deg and the friction coefficient is μ=0.1).

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