Rolling Resistance and Energy Loss in Tyres Mohammad Mehdi Davari [email protected] KTH Vehicle Dynamics Department of Aeronautical and Vehicle Engineering

Total Page:16

File Type:pdf, Size:1020Kb

Rolling Resistance and Energy Loss in Tyres Mohammad Mehdi Davari Mmdavari@Kth.Se KTH Vehicle Dynamics Department of Aeronautical and Vehicle Engineering Rolling resistance and energy loss in tyres Mohammad Mehdi Davari [email protected] KTH Vehicle Dynamics Department of Aeronautical and Vehicle Engineering SVEA seminar May 20, 2015 Contents • Background and challenges • Research objectives • Rolling loss • Tyre models • Modelling process • Results • Summary and conclusions MOHAMMAD MEHDI DAVARI 2015-05-19 2 Vehicle energy usage 8 100 0,38 6 4,14 Inertial forces 1,33 0,78 4,93 km 4 0,76 Aerodynamic forces 0,97 2,24 2,19 Internal frictional forces 2 0,55 0,59 Rolling resistance forces 2,57 0,5 Contribution in liters/ 1,47 1,56 1,38 0 Urban Extraurban Major and minor Motorway roads Every day 2 millions tonnes of fuel burns up to overcome rolling resistance! Source: Michelin MOHAMMAD MEHDI DAVARI 2015-05-19 3 Reducing rolling resistance and consequently the fuel consumption is a major development goal for vehicle and tyre manufactures. MOHAMMAD MEHDI DAVARI 2015-05-19 4 What does the vehicle industry do? Narrower Larger VW XL1: 115/80 R15 Michelin BMW i3: 155/70 R19 Bridgestone MOHAMMAD MEHDI DAVARI 2015-05-19 5 What about the tyre industry? Source: Michelin MOHAMMAD MEHDI DAVARI 2015-05-19 6 …but, there are challenges! Green tyres Source: Michelin MOHAMMAD MEHDI DAVARI 2015-05-19 7 What we as vehicle dynamicists can do to affect the rolling resistance? MOHAMMAD MEHDI DAVARI 2015-05-19 8 Research goal… … presenting an idea, apart from the state-of-the-art methods, to reduce the resistance originated from the tyre. MOHAMMAD MEHDI DAVARI 2015-05-19 9 Research questions • What is an appropriate model to characterise the rolling loss in the tyre during a vehicle manoeuvre? • Is it reasonable to believe that there is any potential to reduce the rolling loss and thereby fuel consumption by using active chassis solutions? MOHAMMAD MEHDI DAVARI 2015-05-19 10 Rolling resistance Main contributors associated with tyre rolling resistance; • Hysteretic losses in the sidewall and the tread • Tyre aerodynamic drag and air circulations • Tyre-road interaction and surface losses Rubber deformation 80 – 95 % Aerodynamic resistance 0 – 15 % Tyre-road interaction <5 % MOHAMMAD MEHDI DAVARI 2015-05-19 11 Rolling resistance In-door measurement Out-door measurement Rolling direction [Source: Technical University of Gdansk] 퐹푟 푓푟 = 퐹푧 푀푦 푀푦 = 퐹푧 ∙ 푒 푓푟 = 퐹푧 ∙ 푧푡 ISO 18164:2005 measuring rolling resistance, under controlled laboratory conditions (free rolling, straight ahead driving, specific load and speed) MOHAMMAD MEHDI DAVARI 2015-05-19 12 A global definition Pressure distribution and shape of the contact patch depend on driving conditions and wheel alignments, thus this coefficient will be a variable dependent to other parameters; 푠푖푑푒 푠푙푖푝 푎푛푔푙푒 푐푎푚푏푒푟 푎푛푔푙푒 푠푙푖푝 푟푎푡푖표 푅표푙푙푖푛푔 푟푒푠푖푠푡푎푛푐푒 푐표푒푓푓푖푐푖푒푛푡 = 푓 푣푒푟푡푖푐푎푙 푙표푎푑 푠푝푒푒푑 푡푒푚푝푒푟푎푡푢푟푒 푚푎푡푒푟푖푎푙 … Therefore, for free-rolling, straight ahead driving and neutral wheel alignment in-plane rolling resistance coefficient (푓푟) will be used instead and in general the term rolling resistance coefficient (푓푅). MOHAMMAD MEHDI DAVARI 2015-05-19 13 Rolling loss “Rolling loss" refers to the energy dissipation in the tyre due to deflections as well the losses in the sliding region. Dissipation sources Adhesion force limit Sliding force limit Adhesion region -a 0 a SlidingSliding region region Contact patch length Internal losses External losses MOHAMMAD MEHDI DAVARI 2015-05-19 14 Tyre models Empirical models Similarity based models Simple physical models Complex physical models Degree of fit Low dependency Independency on number of from number of experiments full scale tests Insight in tyre Simplicity of behaviour formulation Less computational effort MOHAMMAD MEHDI DAVARI 2015-05-19 15 Initialisation Rolling loss Expectations from the model... Tyre Rubber Time Energy observer Inputs Internal loss Bristle External loss • Be applicable within vehicle deflection δ Bristle force Longitudinal speed Vx dynamics simulations. Vertical force F x x level z Vehicle Slip ratio y Rubber model y Total rolling resistance • Considering the rolling loss Side slip angle z z Camber angle Friction observer In-plane rolling resistance in tyre from a holistic level Chassis Chassis approch. Pressure distribution Pressure K Tyre z • Be able to simulate the level (vertical stiffness) Updating Time Quarter car internal and external losses. And model Road roughness Bristle deflection level Road MOHAMMAD MEHDI DAVARI 2015-05-19 16 Modelling process: Dissipation modelling Loss angle Rate Viscoelastic modules dependent Rate Friction modules independent Force Displacement Phase 20 15 10 5 0 Force [N] Force -5 1 Hz -10 10 Hz Friction -15 -20 -0,01 -0,005 0 0,005 0,01 Displacement [m] Rubber model MOHAMMAD MEHDI DAVARI 2015-05-19 17 Modelling process: Tyre modelling Extended Brush tyre Model (EBM) Finite number of Flexible carcass 0.05 lines and bristles 0 -0.05 -0.1 -0.15 Brush tyre Z [m] State observer theory -0.2 -0.25 Lateral force -0.3 Friction ellipse -0.1 -0.05 0 0.05 0.1 Y [m] Maximum Dissipation Rate Mode (MDRM) - Think about animtion - Use bigger fonts MOHAMMAD MEHDI DAVARI 2015-05-19 18 Model algorithm MOHAMMAD MEHDI DAVARI 2015-05-19 19 Results MOHAMMAD MEHDI DAVARI 2015-05-19 20 Global forces Longitudinal slip 6000 5000 The structural behaviour of the 4000 Magic Formula 3000 tyre model represented by the [N] EBM x global forces shows good fit F 2000 with measured data and Magic Formula. 1000 0 0 10 20 30 40 50 60 70 80 90 100 [-] x Combined slip Lateral slip 500 3000 Measured data at = 0 0 EBM at = 0 Measured data at = 6 2000 = -2 -500 EBM at = 6 1000 -1000 Measurement 0 EBM -1500 Measurement [N] [N] y y -1000 EBM -2000 F F -2000 = 4 -2500 -3000 -3000 -3500 -4000 -4000 -4000 -3000 -2000 -1000 0 1000 2000 3000 4000 5000 0 5 10 15 20 25 30 F [N] [deg] x MOHAMMAD MEHDI DAVARI 2015-05-19 21 Detailed study of contact patch = 0 , = 0 4 0.15 Inner edge x 10 0 0.1 0.05 5 [Pa] z 0 p 10 -0.05 Contact width [m] width Contact 15 -0.1 = 0 -0.1 -0.05 0.1 = -2 0 0.05 -0.15 Outer edge 0.05 0 = -3 -0.05 0.1 -0.1 -0.1 -0.05 0 0.05 0.1 0.15 y[m] x[m] Contact length [m] Make another movie to prevent flickering MOHAMMAD MEHDI DAVARI 2015-05-19 22 Influence of vehicle level parameters: speed 0.025 0.02 EBM FEM 0.02 0.015 0.015 0.01 0.01 0.005 0.005 Rollingresistance coefficient [-] Rollingresistance coefficient [-] Rubber A Rubber a Rubber B Rubber b Rubber C Rubber c 0 0 0 10 20 30 40 50 5 10 15 20 25 30 35 40 Velocity [m/s] Velocity[ m/s] MOHAMMAD MEHDI DAVARI 2015-05-19 23 Influence of vehicle level parameters: load and torque 0.019 0.0185 0.018 0.0175 0.017 0.0165 Rollingresistance coefficient [-] 0.016 0.0155 2000 3000 4000 5000 6000 7000 8000 Vertical force [N] 4000 3500 3000 2500 2000 1500 1000 500 Energy loss per unit distance travelled [J/m] travelleddistance unit lossper Energy 0 -6000 -4000 -2000 0 2000 4000 6000 Fx [N] Braking Driving MOHAMMAD MEHDI DAVARI 2015-05-19 24 Influence of chassis and tyre level parameters 0.0146 0.16 0.0145 0.14 0.0145 0.12 0.0144 0.1 0.0144 0.08 0.0143 0.06 0.0143 0.04 0.0142 0.02 Rollingresistance coefficient [-] Rollingresistance coefficient [-] 0.0142 0 -6 -4 -2 0 2 4 6 -6 -4 -2 0 2 4 6 Camber angle [deg] Side slip angle [deg] 0.035 0.03 0.025 Tyre pressure and 0.02 vertical stiffness are linearly dependent 0.015 푃 ∝ 푘푧 0.01 Rollingresistance coefficient [-] 0.005 0.4 0.6 0.8 1 1.2 1.4 1.6 1.8 2 Relative vertical stiffness [-] MOHAMMAD MEHDI DAVARI 2015-05-19 25 Energy studies 1800 Longitudinal dissipation =0 [deg] 1600 Lateral dissipation =0 [deg] 훼 1400 Vertical dissipation =0 [deg] Longitudinal dissipation =2 [deg] 1200 Lateral dissipation =2 [deg] 1000 Vertical dissipation =2 [deg] 800 600 Total dissipated energy Total [J]dissipated energy 400 200 0 0 0.2 0.4 0.6 0.8 1 1.2 1.4 1.6 1.8 2 Time [s] MOHAMMAD MEHDI DAVARI 2015-05-19 26 2000 0.04 Dynamic maneouvres 1000 =0 0.03 0 =-2 [N] 0.02 y Steering angle F -1000 0.01 -2000 0 1 1.5 2 2.5 [rad] angle Steering 56 =0 54 5 N 10,0% =-2 [N] r F 52 50 1 1.5 2 2.5 2000 =0 -19,0% =-2 435 N [N] R 1000 F 0 1 1.5 2 2.5 1000 =0 30 W -2,5% =-2 900 800 Internal lossInternal [W] rate 1 1.5 2 2.5 1000 =0 -11,5% 72 W 500 =-2 0 External loss [W] rate 1 1.5 2 2.5 훾 = 0° Time [s] MOHAMMAD MEHDI DAVARI 2015-05-19 27 Internal Loss (E) Internal Loss Rate (dE/dt) 1 1 = 0 = 0 = -2 = -2 [J] 0 0 x /dt [W] x E dE -1 -1 0 0.5 1 1.5 2 2.5 3 3.5 1 1.5 2 2.5 40 100 [J] 20 y /dt [W] 50 y E dE 0 0 0 0.5 1 1.5 2 2.5 3 3.5 1 1.5 2 2.5 3000 950 1421 2000 1420.5 [J] z 900 1420 /dt [W] z E 1000 1419.5 dE 1.6119 1.612 1.6121 0 850 0 0.5 1 1.5 2 2.5 3 3.5 1 1.5 2 2.5 3000 1000 2000 1620 1615 950 E [J] 1000 1610 dE/dt [W] 900 1.802 1.804 1.806 0 0 0.5 1 1.5 2 2.5 3 3.5 1 1.5 2 2.5 time time MOHAMMAD MEHDI DAVARI 2015-05-19 28 Summary and future work Internal losses Parametrising the Implementation rolling resistance External losses Tyre modelling Control strategies Rolling losses Rolling loss Rolling loss studies in full modelling vehicle MOHAMMAD MEHDI DAVARI 2015-05-19 29 Conclusion • A tyre model to investigate the rolling loss is presented.
Recommended publications
  • Tire Manual.Pdf
    Revision Highlights The FedEx Tire Manual has content changes including the following: Chapter 1: Purchasing Jun 2008 1-10: Added Q & A FILING WARRANTY ON TIRES NOT MOUNTED Chapter 2: Warranty Chapter 3: Tire Applications Jun 2008 3-10: Updated Product Codes and Drive Tire Design 3-15: Added Toyota Specs to Cargo Tractors Chapter 4: Maintenance . Chapter 5: Shop Administration . Contents ii Contents Publication Information ........................................................................................................................ vi Chapter 1: Purchasing .......................................................................................................................... 1 1-5: Tire Ordering Process ....................................................................................................................................... 2 Filing Claims – Tires Lost in Shipment ........................................................................................................ 2 Contact Numbers and Procedures .............................................................................................................. 4 1-10: Frequently Asked Questions - Goodyear Tires ............................................................................................... 5 Double Shipment on Tires ........................................................................................................................... 5 Ordered Wrong or Wrong Tires Shipped ...................................................................................................
    [Show full text]
  • Rolling Resistance During Cornering - Impact of Lateral Forces for Heavy- Duty Vehicles
    DEGREE PROJECT IN MASTER;S PROGRAMME, APPLIED AND COMPUTATIONAL MATHEMATICS 120 CREDITS, SECOND CYCLE STOCKHOLM, SWEDEN 2015 Rolling resistance during cornering - impact of lateral forces for heavy- duty vehicles HELENA OLOFSON KTH ROYAL INSTITUTE OF TECHNOLOGY SCHOOL OF ENGINEERING SCIENCES Rolling resistance during cornering - impact of lateral forces for heavy-duty vehicles HELENA OLOFSON Master’s Thesis in Optimization and Systems Theory (30 ECTS credits) Master's Programme, Applied and Computational Mathematics (120 credits) Royal Institute of Technology year 2015 Supervisor at Scania AB: Anders Jensen Supervisor at KTH was Xiaoming Hu Examiner was Xiaoming Hu TRITA-MAT-E 2015:82 ISRN-KTH/MAT/E--15/82--SE Royal Institute of Technology SCI School of Engineering Sciences KTH SCI SE-100 44 Stockholm, Sweden URL: www.kth.se/sci iii Abstract We consider first the single-track bicycle model and state relations between the tires’ lateral forces and the turning radius. From the tire model, a relation between the lateral forces and slip angles is obtained. The extra rolling resis- tance forces from cornering are by linear approximation obtained as a function of the slip angles. The bicycle model is validated against the Magic-formula tire model from Adams. The bicycle model is then applied on an optimization problem, where the optimal velocity for a track for some given test cases is determined such that the energy loss is as small as possible. Results are presented for how much fuel it is possible to save by driving with optimal velocity compared to fixed average velocity. The optimization problem is applied to a specific laden truck.
    [Show full text]
  • Chapter 4 Vehicle Dynamics
    Chapter 4 Vehicle Dynamics 4.1. Introduction In order to design a controller, a good representative model of the system is needed. A vehicle mathematical model, which is appropriate for both acceleration and deceleration, is described in this section. This model will be used for design of control laws and computer simulations. Although the model considered here is relatively simple, it retains the essential dynamics of the system. 4.2. System Dynamics The model identifies the wheel speed and vehicle speed as state variables, and it identifies the torque applied to the wheel as the input variable. The two state variables in this model are associated with one-wheel rotational dynamics and linear vehicle dynamics. The state equations are the result of the application of Newton’s law to wheel and vehicle dynamics. 4.2.1. Wheel Dynamics The dynamic equation for the angular motion of the wheel is w& w =[Te - Tb - RwFt - RwFw]/ Jw (4.1) where Jw is the moment of inertia of the wheel, w w is the angular velocity of the wheel, the overdot indicates differentiation with respect to time, and the other quantities are defined in Table 4.1. 31 Table 4.1. Wheel Parameters Rw Radius of the wheel Nv Normal reaction force from the ground Te Shaft torque from the engine Tb Brake torque Ft Tractive force Fw Wheel viscous friction Nv direction of vehicle motion wheel rotating clockwise Te Tb Rw Ft + Fw ground Mvg Figure 4.1. Wheel Dynamics (under the influence of engine torque, brake torque, tire tractive force, wheel friction force, normal reaction force from the ground, and gravity force) The total torque acting on the wheel divided by the moment of inertia of the wheel equals the wheel angular acceleration (deceleration).
    [Show full text]
  • Winter Testing in Driving Simulators
    ViP publication 2017-2 Winter testing in driving simulators Authors Fredrik Bruzelius, VTI Artem Kusachov, VTI www.vipsimulation.se ViP publication 2017-2 Winter testing in driving simulators Authors Fredrik Bruzelius, VTI Artem Kusachov, VTI www.vipsimulation.se Cover picture: Original photo by Hejdlösa Bilder AB, edited by Artem Kusachov Reg. No., VTI: 2014/0006-8.1 Printed in Sweden by VTI, Linköping 2018 Preface The project Winter testing in driving simulator (WinterSim) was a PhD student project carried out by the Swedish National Road and Transport Research Institute (VTI) within the ViP Driving Simulation Centre (www.vipsimualtion.se). The focus of the project was to enable a realistic winter simulation environment by studying the required components and suggesting improvements to the current common practice. Two main directions were studied, motion cueing and tire dynamics. WinterSim started in November 2014 and lasted for three years, ending in December 2016. Findings from both research directions have been published in journals and at scientific conferences, and the project resulted in the licentiate thesis “Motion Perception and Tire Models for Winter Conditions in Driving Simulators” (Kusachov, 2016). This report summarises the thesis and the undertaken work, i.e. gives a short overall presentation of the project and the major findings. The WinterSim project was funded up to a licentiate thesis through the ViP competence centre (i.e. by ViP partners and the Swedish Governmental Agency for Innovation Systems, VINNOVA), Test Site Sweden and the internal PhD student program at VTI. The project was carried out by Artem Kusachov (PhD student) and Fredrik Bruzelius (project manager and supervisor of the PhD student), both at VTI.
    [Show full text]
  • Tire/Road Rolling Resistance Modeling: Discussing the Surface Macrotexture Effect
    coatings Article Tire/Road Rolling Resistance Modeling: Discussing the Surface Macrotexture Effect Malal Kane * , Ebrahim Riahi and Minh-Tan Do AME-EASE, University Gustave Eiffel, IFSTTAR, F-44344 Bouguenais, France; [email protected] (E.R.); [email protected] (M.-T.D.) * Correspondence: [email protected] Abstract: This paper deals with the modeling of rolling resistance and the analysis of the effect of pavement texture. The Rolling Resistance Model (RRM) is a simplification of the no-slip rate of the Dynamic Friction Model (DFM) based on modeling tire/road contact and is intended to predict the tire/pavement friction at all slip rates. The experimental validation of this approach was performed using a machine simulating tires rolling on road surfaces. The tested pavement surfaces have a wide range of textures from smooth to macro-micro-rough, thus covering all the surfaces likely to be encountered on the roads. A comparison between the experimental rolling resistances and those predicted by the model shows a good correlation, with an R2 exceeding 0.8. A good correlation between the MPD (mean profile depth) of the surfaces and the rolling resistance is also shown. It is also noticed that a random distribution and pointed shape of the summits may also be an inconvenience concerning rolling resistance, thus leading to the conclusion that beyond the macrotexture, the positivity of the texture should also be taken into account. A possible simplification of the model by neglecting the damping part in the constitutive model of the rubber is also noted. Keywords: dynamic friction model; rolling resistance coefficient; macrotexture Citation: Kane, M.; Riahi, E.; Do, M.-T.
    [Show full text]
  • Wheel Slip Control for Improving Traction-Ability and Energy Efficiency of a Personal Electric Vehicle
    Energies 2015, 8, 6820-6840; doi:10.3390/en8076820 OPEN ACCESS energies ISSN 1996-1073 www.mdpi.com/journal/energies Article Wheel Slip Control for Improving Traction-Ability and Energy Efficiency of a Personal Electric Vehicle Kanghyun Nam 1, Yoichi Hori 2 and Choonyoung Lee 3,* 1 School of Mechanical Engineering, Yeungnam University, 280 Daehak-ro, Gyeongsan 712-749, Korea; E-Mail: [email protected] 2 Department of Advanced Energy, Graduate School of Frontier Sciences, the University of Tokyo, Kashiwa, Chiba 277-8561, Japan; E-Mail: [email protected] 3 School of Mechanical Engineering, Kyungpook National University, 80 Daehak-ro, Bukgu, Daegu 702-701, Korea * Author to whom correspondence should be addressed; E-Mail: [email protected]; Tel./Fax: +82-53-950-7541. Academic Editor: Joeri Van Mierlo Received: 20 May 2015 / Accepted: 30 June 2015 / Published: 7 July 2015 Abstract: In this paper, a robust wheel slip control system based on a sliding mode controller is proposed for improving traction-ability and reducing energy consumption during sudden acceleration for a personal electric vehicle. Sliding mode control techniques have been employed widely in the development of a robust wheel slip controller of conventional internal combustion engine vehicles due to their application effectiveness in nonlinear systems and robustness against model uncertainties and disturbances. A practical slip control system which takes advantage of the features of electric motors is proposed and an algorithm for vehicle velocity estimation is also introduced. The vehicle velocity estimator was designed based on rotational wheel dynamics, measurable motor torque, and wheel velocity as well as rule-based logic.
    [Show full text]
  • Michelin® Agriculture and Compact Equipment Tires Technical Data Book | 2019
    MICHELIN® AGRICULTURE AND COMPACT EQUIPMENT TIRES TECHNICAL DATA BOOK | 2019 Business.Michelinman.com Tweel.Michelinman.com Michelin Agriculture Contents TRACTOR TIRES 2-55 SPRAYER & ROW CROP TIRES 76-81 AGRIBIB® 2SPRAYBIB™ 76 AGRIBIB® 2 12 AGRIBIB® ROW CROP 79 YIELDBIB™ 17 MACHXBIB® 21 AXIOBIB® 26 AXIOBIB® 2 31 MULTIBIB™ 36 OMNIBIB™ 43 XEOBIB® 48 ROADBIB® 52 TRAILERS & IMPLEMENTS 82-93 EVOBIB® 54 CARGOXBIB® HIGH FLOTATION 82 CARGOXBIB® HEAVY DUTY 86 CARGOXBIB® 87 XP27™ 90 XS™ 92 HARVESTER & FLOATER TIRES 56-74 CEREXBIB™ 2 56 CEREXBIB™ 61 FLOATXBIB 66 MEGAXBIB® 2 68 MEGAXBIB® 71 TIRE TECHNICAL DATA BOOK | 2019 COMPACT EQUIPMENT TIRES 94-132 OPERATIONAL INFORMATION 133-153 XMCL™ 99 SIZE EQUIVALENCY CHART 134 XM27™ 104 ROLLING CIRCUMFERENCE INDEX CHART 135 BIBLOAD® HARD SURFACE 105 TIRE SIDEWALL MARKINGS 138 CROSSGRIP® 109 LOAD INDICES AND SPEED RATINGS 139 XF™ 112 OPERATING INSTRUCTIONS 140 XM47™ 114 CALCULATION OF MECHANICAL LEAD (4WD) 141 POWER CL™ 116 LOAD-BALANCING CALCULATION 142 POWER DIGGER 121 RIM AND O-RING REFERENCES 144 BIBSTEEL™ ALL TERRAIN 123 VALVE CHARACTERISTICS 145 BIBSTEEL™ HARD SURFACE 125 MICHELIN® TUBES 147 X® TWEEL® SSL 2 127 MOUNTING / DISMOUNTING 149 X® TWEEL® TURF 129 X® TWEEL® TURF CASTER 130 X® TWEEL® UTV 131 X® TWEEL® TURF – GOLF CART 132 TIRE TECHNICAL DATA BOOK | 2019 Reading the technical data Charts Specifi c markings for high technology tires • IF: Increased Flexion (Tires designed to carry 20% more load at the same pressure or 20% less pressure for the same load compared to standard radials in the same size) • VF: Very High Flexion (Tires designed to carry 40% more load at the same pressure or 40% less pressure for the same load compared to standard radials in the same size) • CFO & CFO+: Improved Flexion Cyclic Field Operation (Cyclic Field Operating parameters for IF and VF designated tires) Rim Local country diameter (TL) & international in inches Tubeless product code Rim Size (inch) Description MSPN (CAI) 38 IF 710/85 R38 178D TL 99013 (992951) Section Overall Loaded Rolling Recommended Acceptable Min.
    [Show full text]
  • Installation for You
    IMPORTANT – MUST READ BEFORE INSTALLING Nitromousse is FOR OFF-ROAD USE ONLY! Nitromousse is NEVER to be used for on-road, or on- highway use. A proper fitting rim lock must be used with Nitromousse to prevent tire slip, DO NOT MOUNT a Nitromousse without a proper fitting and functioning rim lock. Use all of the supplied lubricant when mounting a Nitromousse. Apply half of the tube to the inside of the tire and the other half to the outside of the mousse. Make sure to plug any unused holes in the rim or the lubricant will seep out. Never mount a Nitromousse without proper lubrication. Installing a mousse will require the correct tools and proper technique. - If you do not have correct tools or are not confident in installing or changing a mousse, we strongly recommend that you have a qualified shop or mechanic perform the installation for you. TIRE SIZE VARIANCE: It is important to note that actual tire sizes can vary from brand to brand and model to model even though they are all marked as the same size. Nitromousse should fit most of the tires that they are sized for (but not all). Once installed inside the tire, the Nitromousse should have a very snug fit without any play or gaps between it and the tire. If the Nitromousse is too small for the tire, we suggest going up a size or it will feel too soft and make the tire feel unstable, this can also cause premature wear to the Nitromousse. If a Nitromousse is used on hard surfaces at high speeds it is important to remove and re-lube after each days use and at the same time inspect it for wear or damage and replace if necessary.
    [Show full text]
  • ROLLING RESISTANCE Factors Affecting Roiling Resistance
    FUNDAMENTALS OF VEHICLE DYNAMICS CHAPTER 4 - ROAD LOADS Effective tire cornering stiffness is favorably influenced directly by using tires Considering the vehicle as a whole, the total rolling resistance is the sum with high cornering stiffness and by eliminating compliances in the steering or of the resistances from all the wheels: suspension which allow the vehicle to yield to the crosswind. However, the moment arm is strongly diminished by forward speed, thereby tending to (4-1 2) increase crosswind sensitivity as speed goes up. where: The static analysis discussed above may overlook certain other vehicle Rxf = Rolling resistance of the front wheels dynamic properties that can influence crosswind sensitivity. Roll compliance, particularly when it induces suspension roll steer effects, may playa significant Rxr = Rolling resistance of the rear wheels role not included in the simplified analysis. Thus a more comprehensive fr = Rolling resistance coefficient analysis using computer models of the complete dynamic vehicle and its aerodynamic properties may be necessary for more accurate prediction of a W Weight of the vehicle vehicle's crosswind sensitivity. For theoretically correct calculations, the dynamic weight of the v ·hick. including the effects of acceleration, trailer towing forces and the v 'flin t! component of air resistance, is used. However, for vehicle perfOJ'lIl;tIH'I' estimation, the changing magnitude of the dynamic weight complical ' S IIII' ROLLING RESISTANCE calculations without offering significant improvements in accuracy. hlJ Ih"1 more, the dynamic weight transfer between axles has minimal intluenc '0111111' The other major vehicle resistance force on level ground is the rolling total rolling resistance (aerodynamic lift neglected).
    [Show full text]
  • Low Pressure Revolution
    2005 ISSUE BONUS Vol. XVIV, No. 6 November-December 2004 Comitted to Ecological Backcountry Travel Since 1984 FOURWHEELING ACADEMY FOURWHEELING ACADEMY RANCHO Low Pressure RS99700 Revolution NEW REMOTE CONTROL PANEL AND FITTINGS FOR RANCHO RS9000X SERIES SHOCKS EDITOR'S NOTE:The Ol' Coyote is pretty slow on social things. For By Harry Lewellyn years I've been doing these articles with the If you have been on many of my tours, help of friends, but you’ll know that you regularly get the seldom have provided Rancho 9000X cab adjustment pitch when proper credit. “From the we hit the washboard. I typically let you Coyote” on page 2 know that via the remote control, I can sig- thanks the players. They nificantly smooth out the annoying ride by deserve recognition. adjusting my shocks to maximum soft from within the cab, while moving. The annoying “brrrit” (trill your tongue) all but goes away. What’s new is that Rancho has By Harry Lewellyn changed the control panel, pump and tub- ing, and gone to easier, more secure snap Staun Products' Internal fittings. BeadLock™ is creating a low I’ll start in the cab, run you through tire pressure revolution. Words the firewall and out to the pump, and final- alone don't do this product jus- ly, to the shocks. Figure 1 Staun’s Internal, pneumatic BeadLock™ tice. Even if you don't read the RS99700 KIT entire article, take a look at the was awarded “Best Product Under $250” in 2004 by The kit has everything including new pictures. They are very impres- Australia’s 4WD Monthly magazine.
    [Show full text]
  • Carbon Fiber Racing Wheels Assembly Instructions
    Orders: 1-877-GO-HIPER Carbon Fiber Racing Wheels Local: (785)-749-6011 Fax: (785)-749-4760 Assembly Instructions www.hiper-technology.com Wheel Parts List: Part Quantity Aluminum Center Section 1 Carbon Fiber Wheel Half 2 Carbon Fiber Bead-Lock Ring 1- Single Bead-Lock Wheel, 2- Dual Bead-Lock Wheel Stainless Steel Bolt – ¼”-28 x 1.25 12 Stainless Steel Bolt – ¼”-28 x 1.00 12- Single Bead-Lock Wheel, 24- Dual Bead-Lock Wheel Chro-Moly Steel Nut – ¼”-28 12 Valve Stem 1 Rubber O-Rings 2 Tools and Supplies Required: 1. 3/8” Socket (12 point) (3/8” Drive) 2. Ratchet and Extension (3/8” Drive) 4. WD-40 Lubricant and/or liquid dish soap. 3. Cordless Drill with ¼” Drive attachment 5. Screw Driver or Tire Spoons (Recommended). preferred. Torque Specs and Torque Patterns: (NOTE: DO NOT EXCEED TORQUE SPECIFICATIONS) Center Section – Torque center section bolts with 3/8 ” drive ratchet, maximum 9 - 11 ft-lbs (108 – 132 in-lbs) in a two-stage star or criss-cross pattern. Bead-Lock Ring – Torque bead-lock ring bolts with 3/8” drive ratchet, maximum 8 - 11 ft-lbs (96 – 132 in-lbs), using circular pattern will assist in aligning the bead. Lug Nuts – Torque lug nuts to a maximum of 50 ft lbs. Tire Mounting: Use Tire Mounting Lubricant on Non-Bead-Lock half when mounting the tire. WD-40 Lubricant and/or liquid dish soap will work also. CAUTION: Do not exceed recommended tire pressure for seating the tire bead, and/or 25psi. Returns: All Returns will require a return material authorization number (RMA).
    [Show full text]
  • PHENOMENA of PNEUMATIC TIRE HYDROPLANING by Walter B
    https://ntrs.nasa.gov/search.jsp?R=19640000612 2020-03-11T16:26:55+00:00Z View metadata, citation and similar papers at core.ac.uk brought to you by CORE provided by NASA Technical Reports Server NASA TECHNICAL NOTE NASA TN D-2056 t.f-t | Z t--- Z PHENOMENA OF PNEUMATIC TIRE HYDROPLANING by Walter B. Horne and Robert C. Dreher Langley Research Center Langley Station, Hampton, Va° NATIONAL AERONAUTICSAND SPACEADMINISTRATION • WASHINGTON, D. C. • NOVEMBER 1963 TECHNICAL NOTE D-2056 PHENOMENA OF PNEUMATIC TIRE HYDROPLANING By Walter B. Horne and Robert C. Dreher Langley Research Center Langley Station, Hampton, Va. NATIONAL AERONAUTICS AND SPACE ADMINISTRATION PHENOMENA OF PNEUMATIC TIRE HYDROPLANING By Walter B. Home and Robert C. Dreher SUMMARY Recent research on pneumatic tire hydroplaning has been collected and sum- marized with the aim of describing what is presently known about the phenomena of tire hydroplaning. A physical description of tire hydroplaning is given along with formulae for estimating the ground speed at which it occurs. Eight manifes- tations of tire hydroplaning which have been experimentally observed are pre- sented and discussed. These manifestations are: detachment of tire footprint, hydrodynamic ground pressure, spin-down of wheel, suppression of tire bow wave, scouring action of escaping fluid in tire-ground footprint region, peaking of fluid displacement drag, loss in braking traction, and loss of tire directional stability. The vehicle_ pavement, tire, and fluid parameters of importance to tire hydroplaning are listed and described. Finally, the hazards of tire hydro- planing to ground and air-vehicle-ground performance are listed, and procedures are given to minimize these effects.
    [Show full text]