Study of Roll Center Saurabh Singh*, Sagar Sahu**

Total Page:16

File Type:pdf, Size:1020Kb

Study of Roll Center Saurabh Singh*, Sagar Sahu** Imperial International Journal of Eco-friendly Technologies Vol.- 1, Issue-1(2016), pp.38-43 IIJET STUDY OF ROLL CENTER SAURABH SINGH*, SAGAR SAHU** *, **Mechanical engineering, NIT B ABSTRACT roll center can be an actual pivot point or a virtual point in space and they don’t essentially lie along the center line of As our solar car aims to bring new green technology to cope the vehicle. SAE’s definition indicates, if the roll centers of a up with the greatest challenge of modern era i.e. energy car are at the same height as the sprung mass’ Center of demand and ESVC is a racing championship of such Gravity (CG), it will not reveal any body roll during a corner innovative technology that bring thrills on speed but in an a line connecting the rear suspension roll Centre with that of ecofriendly way. As much it is important to bring speed to the front is called the roll axis. car so as equally important to design and fabricate vehicle design so that it can withstand high speeds to let it run and flow smoothly. That is the work of suspension system to keep the optimal tire contact with ground and keep passengers comfortable and one of the most important aspect of which is Roll Center. The vehicle roll center is a key parameter that influences the vehicle roll dynamics. The roll center is considered an important factor in determining overall vehicle ride and handling quality it is important to know how to find Fig. 1: Roll Center roll center for different type of suspension. So it becomes important for vehicle discuss roll center with respect to different suspension parameter and relation between roll center and center of gravity with changing vertical position of roll center for front and rear suspension system. I. INTRODUCTION Roll center of a vehicle is the imaginary but accurately defined point on the center-line of the car around which the Fig. 2: Roll Axis Location vehicle rolls, at which the cornering forces in the suspension system are transferred to the vehicle body. The location of Reason to find the Roll Center of a car is about predicting the geometric roll center is solely dictated by the suspension how the car reacts while cornering. Knowing where the roll geometry. The official definition of roll center are- center is in the front of the car gives an idea of what the wheels will be doing as the nose of the car dives under •SAE: a point in the transverse plane through any pair of braking or leans in a corner. Without roll center information, wheels at which a transverse force may be applied to the one cannot estimate how much the camber angle of the front sprung mass without causing it to suspension roll. wheels will change during suspension travel or how much body roll will be present while cornering. Roll center is used •Kinematics: the roll is the point about which the body can to determine the stiffness of spring, ride frequency and roll without any lateral movement at either of the wheel various suspension parameters and geometries that will help contact areas. to keep optimal tire contact in both the conditions of ride( a The roll Centre can be high off the ground, low, or even car’s ability to smooth out a bumpy road) and handling ( a below the ground. Depending on the type of suspension, the car’s ability to safely accelerate , brake and corner.) 38 Imperial International Journal of Eco-friendly Technologies Vol.- 1, Issue-1(2016), pp.38-43 IIJET So, the distance between roll center and CoG should be minimum but simultaneously, it is important to keep the minimum distance of roll center from ground in order to minimize jacking forces. To keep our solar car stable in order to negotiate any turn at high speed and keeping above factors in mind, we have performed following iteration on LOTUS SHARK SUSPENSION SOFTWARE and obtained satisfactory value of roll center distance under permissible limit as per our calculations. Fig. 3- Physics Behind Roll Center If N1 and N2 are the normal reaction forces of tires during cornering of vehicle and 2a is the front track width of car, the distance between center of gravity (CoG) and roll center (RC) is L, then to avoid rolling :- N1*a – N2a > F*L ------------------ (1) Where F = mv2/r (centrifugal force) N1 = static normal + lateral load Fig. 5- Results obtained Reaction transfer N2= static normal – lateral load Many of such iterations were performed in order to determine Reaction transfer the appropriate height of roll center from ground. Where, lateral load = m*f*(L+x)/ 2a Transfer Roll-Centre Determination Here m= mass supported on one wheel f= lateral • Aronhold–Kennedy theorem of three centers: when three acceleration of car L+x= height of CoG from ground 2a= track bodies move relative to one another they have three width instantaneous centers all of which lie on the same straight line. The value of L as obtained from equation 1 will give the • Iwb can be varied by angling the upper and lower maximum permissible value of distance of roll center wishbones to different positions, thereby altering the load from CoG in any dynamic condition. transfer between inner and outer wheels in a cornering In any condition, if the distance increases from the maneuver. maximum permissible value, then tire will start losing • This gives the suspension designer some control over the contact with the ground and vehicle would become handling capabilities of a vehicle. unstable. Fig. 4- Iterations performed 39 Imperial International Journal of Eco-friendly Technologies Vol.- 1, Issue-1(2016), pp.38-43 IIJET Instantaneous Center:-Each wheel of an independent In case of double wishbone suspension with Parallel suspension has an instantaneous center and it is the point in horizontal links:- space that the wheel rotates about as the suspension compresses or rebounds. Point Iwb is sometimes referred to And with inclined parallel links :> as 'virtual pivot', or as 'instantaneous center'. The instantaneous center dictates scrub radius, camber change and the way forces are transmitted. This pole can give us information about how the suspension moves. The distance from point Iwb to the centerline of the tire is sometimes referred to as 'swing axle length’, it's as if the hub/wheel is attached to an imaginary swing axle which hinges around point I. Having that long swing axle would be equivalent to having the double wishbone-type suspension, but the actual construction would be very impractical. Nevertheless it Swing axle roll center is located above the “virtual” serves as a good simplification. The swing axle length, joint of the axle. together with the angle, determine the amount of camber change the wheel will experience during the compression of the suspension. A long swing axle length will cause very little camber change as the suspension is compressed, and a very short one will cause a lot. If the upper link and the A- arm are perfectly parallel to each other the intersection point Iwb is infinitely far removed from the car. This isn't a problem though: just draw line as above .these two lines should always intersect on the side of the center of the car, if The roll center for a leaf spring suspension is found by they intersect on the outside, camber change will go from negative to positive back to negative, which is not a good drawing a line between the center of the forward thing for the consistency of the traction. Having a suspension attachment point (A) and the center of the upper that gains negative camber as the body of the car rolls is shackle attachment point (B). Where that line crosses beneficial. It helps keep the tire perpendicular to the ground the vertical center line of the axle is the roll center. The during cornering which maximizes tire contact with the track. roll center height is the vertical distance from the ground to roll center Roll-Centre determination for different type of suspension:- An important point to note that the roll center will move when the suspension is compressed or lifted, that's why it's •In the case of the MacPherson strut suspension the actually an instantaneous roll center. How much this roll upper line defining Iwb is perpendicular to the strut axis center moves as the suspension is compressed is determined by the suspension arm length and the angle between the top and bottom suspension arms (or turnbuckles). As the suspension is compressed, the roll center will become higher and the moment arm (distance between roll center and the car's center of gravity (CoG in the picture)) will decrease. This will mean that as the suspension is compressed (when taking a corner, for example), the car will have less tendency to keep rolling (which is good, you do not want to roll over). When using higher grip tires, the suspension arms should be set in such a way that the roll center is raised significantly as the suspension is compressed. Running parallel, equal-length suspension arms will result in a fixed roll center. This means that as the car leans over, the moment arm will be forcing the 40 Imperial International Journal of Eco-friendly Technologies Vol.- 1, Issue-1(2016), pp.38-43 IIJET car to roll more and more. As a general rule of thumb, the roll moment. Note that it is always the vertical distance higher the center of gravity of your car, the higher the roll between the CG and the RC since the forces always work center should be to avoid a roll-over.
Recommended publications
  • Towards Adaptive and Directable Control of Simulated Creatures Yeuhi Abe AKER
    --A Towards Adaptive and Directable Control of Simulated Creatures by Yeuhi Abe Submitted to the Department of Electrical Engineering and Computer Science in partial fulfillment of the requirements for the degree of Master of Science in Computer Science and Engineering at the MASSACHUSETTS INSTITUTE OF TECHNOLOGY February 2007 © Massachusetts Institute of Technology 2007. All rights reserved. Author ....... Departmet of Electrical Engineering and Computer Science Febri- '. 2007 Certified by Jovan Popovid Associate Professor or Accepted by........... Arthur C.Smith Chairman, Department Committee on Graduate Students MASSACHUSETTS INSTInfrE OF TECHNOLOGY APR 3 0 2007 AKER LIBRARIES Towards Adaptive and Directable Control of Simulated Creatures by Yeuhi Abe Submitted to the Department of Electrical Engineering and Computer Science on February 2, 2007, in partial fulfillment of the requirements for the degree of Master of Science in Computer Science and Engineering Abstract Interactive animation is used ubiquitously for entertainment and for the communi- cation of ideas. Active creatures, such as humans, robots, and animals, are often at the heart of such animation and are required to interact in compelling and lifelike ways with their virtual environment. Physical simulation handles such interaction correctly, with a principled approach that adapts easily to different circumstances, changing environments, and unexpected disturbances. However, developing robust control strategies that result in natural motion of active creatures within physical simulation has proved to be a difficult problem. To address this issue, a new and ver- satile algorithm for the low-level control of animated characters has been developed and tested. It simplifies the process of creating control strategies by automatically ac- counting for many parameters of the simulation, including the physical properties of the creature and the contact forces between the creature and the virtual environment.
    [Show full text]
  • 7.6 Moments and Center of Mass in This Section We Want to find a Point on Which a Thin Plate of Any Given Shape Balances Horizontally As in Figure 7.6.1
    Arkansas Tech University MATH 2924: Calculus II Dr. Marcel B. Finan 7.6 Moments and Center of Mass In this section we want to find a point on which a thin plate of any given shape balances horizontally as in Figure 7.6.1. Figure 7.6.1 The center of mass is the so-called \balancing point" of an object (or sys- tem.) For example, when two children are sitting on a seesaw, the point at which the seesaw balances, i.e. becomes horizontal is the center of mass of the seesaw. Discrete Point Masses: One Dimensional Case Consider again the example of two children of mass m1 and m2 sitting on each side of a seesaw. It can be shown experimentally that the center of mass is a point P on the seesaw such that m1d1 = m2d2 where d1 and d2 are the distances from m1 and m2 to P respectively. See Figure 7.6.2. In order to generalize this concept, we introduce an x−axis with points m1 and m2 located at points with coordinates x1 and x2 with x1 < x2: Figure 7.6.2 1 Since P is the balancing point, we must have m1(x − x1) = m2(x2 − x): Solving for x we find m x + m x x = 1 1 2 2 : m1 + m2 The product mixi is called the moment of mi about the origin. The above result can be extended to a system with many points as follows: The center of mass of a system of n point-masses m1; m2; ··· ; mn located at x1; x2; ··· ; xn along the x−axis is given by the formula n X mixi i=1 Mo x = n = X m mi i=1 n X where the sum Mo = mixi is called the moment of the system about i=1 Pn the origin and m = i=1 mn is the total mass.
    [Show full text]
  • Meritor® Independent Front Suspension Drivetrain System
    MERITOR® INDEPENDENT FRONT SUSPENSION DRIVETRAIN SYSTEM Meritor’s state-of-the-art modular drivetrain system for all-wheel drive (AWD) commercial trucks features the Independent Front Suspension (IFS) module equipped with modern steering geometry and air disc brake technology, and a low-profile shift on-the-fly transfer case. The IFS, available in drive or non-drive options, is a part of Meritor’s field-proven and widely acclaimed ProTec™ ISAS® line of independent suspensions. This bolt-on, modular solution does not require modifications to existing frame rails and maintains vehicle ride height. FEATURES AND BENEFITS ■ Proven Independent Suspension Axle System technology – The ISAS product line has been fitted on high-mobility vehicles for over 20 years. The Independent Front Suspension system leverages decades of expertise in designing and manufacturing field-proven systems. ■ Bolt-on system – The Independent Front Suspension does not require modifications to frame rails ■ 5 to 12 inch ride height reduction – Improves vehicle roll stability versus best-in-class beam axle ■ Modular solution – Maintains the same ride height of a rear-wheel drive (RWD) truck ■ Lower center of gravity – Better vehicle maneuverability and stability for safe and confident handling ■ 60 percent reduction in cab and driver-absorbed power – Ride harshness improvements as well as reduction in unwanted steering feedback lead to less physical fatigue for the driver, and higher reliability of the cab ■ 2-times the wheel travel – The Independent Front Suspension provides
    [Show full text]
  • Caster Camber Tire-Wear Angles
    BASIC WHEEL ALIGNMENT odern steering and ples. Therefore, let’s review these basic the effort needed to turn the wheel. suspension systems alignment angles with an eye toward Power steering allows the use of more are great examples of typical complaints and troubleshooting. positive caster than would be accept- solid geometry at able with manual steering. work. Wheel align- Caster Too little caster can make steering ment integrates all the factors of steer- Caster is the tilt of the steering axis of unstable and cause wheel shimmy. Ex- Ming and suspension geometry to pro- each front wheel as viewed from the tremely negative caster and the related vide safe handling, good ride quality side of the vehicle. Caster is measured shimmy can contribute to cupped wear and maximum tire life. in degrees of an angle. If the steering of the front tires. If caster is unequal Front wheel alignment is described axis tilts backward—that is, the upper from side to side, the vehicle will pull in terms of angles formed by steering ball joint or strut mounting point is be- toward the side with less positive (or and suspension components. Tradi- hind the lower ball joint—the caster more negative) caster. Remember this tionally, five alignment angles are angle is positive. If the steering axis tilts when troubleshooting a complaint of checked at the front wheels—caster, forward, the caster angle is negative. vehicle pull or wander. camber, toe, steering axis inclination Caster is not measured for rear wheels. (SAI) and toe-out on turns. When we Caster affects straightline stability Camber move from two-wheel to four-wheel and steering wheel return.
    [Show full text]
  • Wheel Alignment Simplified
    The WHAT and WHY of Toe Caster - Camber Kingpin Inclination - Thrust Angle Steering Angle – Wheel setback WHEEL ALIGNMENT SIMPLIFIED Wheel alignment is often considered complicated and hard to understand In the days of the rigid chassis construction with solid axles, when tyres were poor and road speeds were low, wheel alignment was simply a matter of ensuring that the wheels rolled along the road in parallel paths. This was easily accomplished by means of using a toe gauge or simple tape measure. The steering wheel could then also simply be repositioned on the splines of the steering shaft. Camber and Caster was easily adjustable by means of shims. Today wheel alignment is of course more sophisticated as there are several angles to consider when doing wheel alignment on the modern vehicle with Independent suspension systems, good performing tyres and high road speeds. Below are the most common angles and their terminology and for the correction of wheel alignment and the diagnoses thereof, the understanding of the principals of these angles will become necessary. Doing the actual corrections of wheel alignment is a fairly simple task and in many instances it is easily accomplished by some mechanical adjustments. However Wheel Alignment diagnosis is not so straightforward and one will need to understand the interaction between the wheel alignment angles as well as the influence the various angles have on each other. In addition there are also external factors one will need to consider. Wheel Alignment Specifications are normally given in angular values of degrees and minutes A circle consists of 360 segments called DEGREES, symbolized by the indicator ° Each DEGREE again has 60 segments called MINUTES symbolized by the indicator ‘.
    [Show full text]
  • Schaeffler Symposium 2018
    2018 Schaeffler Symposium 9/6/2018 Intelligent Active Roll Control INTELLIGENT ACTIVE ROLL CONTROL SHAUN TATE 1 2018 Schaeffler Symposium 9/6/2018 Intelligent Active Roll Control Production Experience & Awards Series Production – 12V BMW 7 Series 2015 BMW 5 Series 2017 RR Phantom 2018 Series Production – 48V Bentley Bentayga 2015 Audi SQ7 2016 Porsche Panamera 2017 Porsche Cayenne 2017 Bentley Continental 2018 Award‐Winning System German Innovation Award Vehicle Dynamics International Award Auto Test Sieger PACE Award 2016 2016 2016 2017 Feature to Product Mapping Stationary Ride Comfort Feature Adaptive Suspension Setup Agility & Stability Conditions Improvement Control Response Clearance Vertical Acceleration Exit Base Stability / Roll Leveling Acceleration Steering Products ‐ Easy Loading Easy Entry Easy Parking Adapt Ground Adapt Wheel Increase Articulation Load Reduce Acceleration Reduce Lateral Reduce Yaw Adapt Self Adapt Steering Dynamic Body Trailer iARC 2 2018 Schaeffler Symposium 9/6/2018 Intelligent Active Roll Control Market Trends & Features Trend 3: Large Trucks/SUVs/Vans for improved comfort and more safety Weight Trend 2: HEV/EV for improved comfort and system availability Vehicle Trend 1: SUV for improved comfort and agility Vehicle Center of Gravity Selling Features Using Schaeffler iARC System Feature Driving Dynamics Comfort Features ADAS Support L3 / Active Safety ‐ Roll Into m Lane Mode ‐ Self Steering Yaw Ride Stability Body Tilt Control Control Emergency Split Free Speed Road Vehicle Class ‐ Stability Active Control
    [Show full text]
  • Aerodynamic Development of a IUPUI Formula SAE Specification Car with Computational Fluid Dynamics(CFD) Analysis
    Aerodynamic development of a IUPUI Formula SAE specification car with Computational Fluid Dynamics(CFD) analysis Ponnappa Bheemaiah Meederira, Indiana- University Purdue- University. Indianapolis Aerodynamic development of a IUPUI Formula SAE specification car with Computational Fluid Dynamics(CFD) analysis A Directed Project Final Report Submitted to the Faculty Of Purdue School of Engineering and Technology Indianapolis By Ponnappa Bheemaiah Meederira, In partial fulfillment of the requirements for the Degree of Master of Science in Technology Committee Member Approval Signature Date Peter Hylton, Chair Technology _______________________________________ ____________ Andrew Borme Technology _______________________________________ ____________ Ken Rennels Technology _______________________________________ ____________ Aerodynamic development of a IUPUI Formula SAE specification car with Computational 3 Fluid Dynamics(CFD) analysis Table of Contents 1. Abstract ..................................................................................................................................... 4 2. Introduction ............................................................................................................................... 5 3. Problem statement ..................................................................................................................... 7 4. Significance............................................................................................................................... 7 5. Literature review
    [Show full text]
  • Development and Analysis of a Multi-Link Suspension for Racing Applications
    Development and analysis of a multi-link suspension for racing applications W. Lamers DCT 2008.077 Master’s thesis Coach: dr. ir. I.J.M. Besselink (Tu/e) Supervisor: Prof. dr. H. Nijmeijer (Tu/e) Committee members: dr. ir. R.M. van Druten (Tu/e) ir. H. Vun (PDE Automotive) Technische Universiteit Eindhoven Department Mechanical Engineering Dynamics and Control Group Eindhoven, May, 2008 Abstract University teams from around the world compete in the Formula SAE competition with prototype formula vehicles. The vehicles have to be developed, build and tested by the teams. The University Racing Eindhoven team from the Eindhoven University of Technology in The Netherlands competes with the URE04 vehicle in the 2007-2008 season. A new multi-link suspension has to be developed to improve handling, driver feedback and performance. Tyres play a crucial role in vehicle dynamics and therefore are tyre models fitted onto tyre measure- ment data such that they can be used to chose the tyre with the best characteristics, and to develop the suspension kinematics of the vehicle. These tyre models are also used for an analytic vehicle model to analyse the influence of vehicle pa- rameters such as its mass and centre of gravity height to develop a design strategy. Lowering the centre of gravity height is necessary to improve performance during cornering and braking. The development of the suspension kinematics is done by using numerical optimization techniques. The suspension kinematic objectives have to be approached as close as possible by relocating the sus- pension coordinates. The most important improvements of the suspension kinematics are firstly the harmonization of camber dependant kinematics which result in the optimal camber angles of the tyres during driving.
    [Show full text]
  • (Title of the Thesis)*
    Reconfigurable Integrated Control for Urban Vehicles with Different Types of Control Actuation by Mansour Ataei A thesis presented to the University of Waterloo in fulfillment of the thesis requirement for the degree of Doctor of Philosophy in Mechanical and Mechatronics Engineering Waterloo, Ontario, Canada, 2017 © Mansour Ataei 2017 Examining committee membership: The following served on the Examining Committee for this thesis. The decision of the Examining Committee is by majority vote. Supervisors: Prof. Amir Khajepour Professor Mechanical and Mechatronics Department Prof. Soo Jeon Associate Mechanical and Mechatronics Department Professor External Prof. Fengjun Yan Associate McMaster University Examiner: Professor Department of Mechanical Engineering Internal- Prof. Nasser Lashgarian Azad Associate System Design Engineering external: Professor Internal: Prof. William Melek Professor Mechanical and Mechatronics Department Internal: Prof. Ehsan Toyserkani Professor Mechanical and Mechatronics Department ii AUTHOR'S DECLARATION I hereby declare that I am the sole author of this thesis. This is a true copy of the thesis, including any required final revisions, as accepted by my examiners. I understand that my thesis may be made electronically available to the public. iii Abstract Urban vehicles are designed to deal with traffic problems, air pollution, energy consumption, and parking limitations in large cities. They are smaller and narrower than conventional vehicles, and thus more susceptible to rollover and stability issues. This thesis explores the unique dynamic behavior of narrow urban vehicles and different control actuation for vehicle stability to develop new reconfigurable and integrated control strategies for safe and reliable operations of urban vehicles. A novel reconfigurable vehicle model is introduced for the analysis and design of any urban vehicle configuration and also its stability control with any actuation arrangement.
    [Show full text]
  • Remove/Install Rack-And-Pinion Steering 11.3.10 MODEL 203 (Except 203.081 /084 /087 /092 /281 /284 /287 /292) MODEL 209
    AR46.20-P-0600P Remove/install rack-and-pinion steering 11.3.10 MODEL 203 (except 203.081 /084 /087 /092 /281 /284 /287 /292) MODEL 209 P46.20-2123-09 1 Front axle carrier 23b Bolts, retaining plate to front axle 25 Steering coupling 1g Retaining plate carrier 25a Bolt, steering coupling to steering 10a Tie rod joints 23g Bolts, rack-and-pinion steering to shaft 21 Rubber bushing front axle carrier 25f Locking plate 23 Rack-and-pinion steering 23n Tapping plate 80a Lower steering shaft 23a Bolts, retaining plate to front axle 23q Oil lines retainer 105d Exhaust shielding plate carrier Modification notes 29.11.07 Value changed: Bolt, retaining plate of oil line to rack-and- Model 203 *BA46.20-P-1001-01F pinion steering Value changed: Bolted connection, rack-and-pinion *BA46.20-P-1002-01F steering to front axle carrier, 1st stage Value changed: Bolted connection of rack-and-pinion *BA46.20-P-1002-01F steering to front axle carrier, 2nd stage 30.11.07 Torque, retaining plate to front axle carrier incorporated Operation step 23, 24 *BA46.20-P-1004-01F Removing Danger! Risk of death caused by vehicle slipping or Align vehicle between columns of vehicle lift AS00.00-Z-0010-01A toppling off of the lifting platform. and position four support plates at vehicle lift support points specified by vehicle manufacturer. Danger! Risk of accident caused by vehicle starting Secure vehicle to prevent it from moving by AS00.00-Z-0005-01A off by itself when engine is running. Risk of itself.
    [Show full text]
  • A Novel Universal Corner Module for Urban Electric Vehicles: Design, Prototype, and Experiment
    A Novel Universal Corner Module for Urban Electric Vehicles: Design, Prototype, and Experiment by Allison Waters A thesis presented to the University of Waterloo in fulfillment of the thesis requirement for the degree of Master of Applied Science in Mechanical Engineering Waterloo, Ontario, Canada, 2017 c Allison Waters 2017 I hereby declare that I am the sole author of this thesis. This is a true copy of the thesis, including any required final revisions, as accepted by my examiners. I understand that my thesis may be made electronically available to the public. ii Abstract This thesis presents the work of creating and validating a novel corner module for a three-wheeled urban electric vehicle in the tadpole configuration. As the urban population increases, there will be a growing need for compact, personal transportation. While urban electric vehicles are compact, they are inherently less stable when negotiating a turn, and they leave little space for passengers, cargo and crash structures. Corner modules provide an effective solution to increase the space in the cabin and increase the handling capabilities of the vehicle. Many corner module designs have been produced in the hopes of increasing the cabin space and improving the road holding capabilities of the wheel. However, none have been used to increase the turning stability of the vehicle via an active camber mechanism while remaining in an acceptable packaging space. Active camber mechanisms are also not a new concept, but they have not been implemented in a narrow packaging space with relatively large camber angle. Parallel mechanism research and vehicle dynamics theory were combined to generate and analyse this new corner module design.
    [Show full text]
  • Electronic Stability Control Systems for Heavy Vehicles; Proposed Rule
    Vol. 77 Wednesday, No. 100 May 23, 2012 Part III Department of Transportation National Highway Traffic Safety Administration 49 CFR Part 571 Federal Motor Vehicle Safety Standards; Electronic Stability Control Systems for Heavy Vehicles; Proposed Rule VerDate Mar<15>2010 18:07 May 22, 2012 Jkt 226001 PO 00000 Frm 00001 Fmt 4717 Sfmt 4717 E:\FR\FM\23MYP2.SGM 23MYP2 mstockstill on DSK4VPTVN1PROD with PROPOSALS2 30766 Federal Register / Vol. 77, No. 100 / Wednesday, May 23, 2012 / Proposed Rules DEPARTMENT OF TRANSPORTATION New Jersey Avenue SE., West Building A. UMTRI Study Ground Floor, Room W12–140, B. Simulator Study National Highway Traffic Safety Washington, DC 20590–0001 C. NHTSA Track Testing Administration • Hand Delivery or Courier: West 1. Effects of Stability Control Systems— Phase I Building Ground Floor, Room W12–140, 49 CFR Part 571 2. Developing a Dynamic Test Maneuver 1200 New Jersey Avenue SE., between and Performance Measure To Evaluate [Docket No. NHTSA–2012–0065] 9 a.m. and 5 p.m. ET, Monday through Roll Stability—Phase II Friday, except Federal holidays. (a) Test Maneuver Development RIN 2127–AK97 • Fax: (202) 493–2251 (b) Performance Measure Development Instructions: For detailed instructions 3. Developing a Dynamic Test Maneuver Federal Motor Vehicle Safety on submitting comments and additional and Performance Measure To Evaluate Standards; Electronic Stability Control information on the rulemaking process, Yaw Stability—Phase III Systems for Heavy Vehicles see the Public Participation heading of (a) Test Maneuver Development (b) Performance Measure Development the SUPPLEMENTARY INFORMATION AGENCY: National Highway Traffic section 4. Large Bus Testing Safety Administration (NHTSA), of this document.
    [Show full text]