a methodology to simulate automotive disc brake tribology

A methodology to simulate automotive disc brake tribology and emissions

GABRIELE RIVA

Academic dissertation which, with the due permission of the KTH Royal Institute of Tech-

nology, will be submitted for public defence for the Degree of Doctor of Philosophy on Fri-

day 30 October 2020 at 09.00 in Gladan, Brinnelvägen 83, Stockholm.

Doctoral Thesis in Machine Design

KTH Royal Institute of Technology

Stockholm, Sweden 2020

© Gabriele Riva

TRITA-ITM-AVL 2020:39

ISBN 978-91-7873-657-7

Printed by: Universitesservice US-AB, Sweden 2020

v

Abstract

Airborne particle emissions from road vehicles are one of the main issues affecting urban

air quality. Vehicle disc brakes are one of the most important sources of non-exhaust emis-

sions, which have recently been considered to be as important as exhaust emissions. In disc

brakes, the pads are pushed against the rotating disc to slow down the vehicle. The contact

surfaces of the disc and pads are worn, some of the debris becomes airborne and can be

harmful to human health if inhaled. Particle emissions from disc brakes are influenced by a

greater amount of contact phenomena at the sliding interfaces, e.g. friction, wear, contact

temperature, contact pressure and surface topography. Due to the difficulty in accessing the

pad-to-disc contact in the brake system during testing, it is hard to study contact phenom-

ena. Moreover, experiments need the friction material and brake system to be produced at

least in their prototype configuration. The aim of this thesis is to develop a methodology

based on simulation to better understand contact phenomena and to evaluate the tribologi-

cal and emission performance of friction material and brake systems in the early design

phase.

Different simulation approaches can be adopted, depending on what is to be evaluated.

A macro-scale approach based on finite element analysis (FEA) can be used to evaluate

wear, particle emission and the coefficient of friction (COF) of the entire brake system. A

meso-scale approach based on cellular automaton (CA) simulation can be used to evaluate

the local contact behaviour on the disc and pad surfaces, and the influence of the single

components of the friction mixture. These two different-scale simulation approaches can be

integrated to generate an overall multi-scale simulation procedure to investigate and predict

the contact phenomena in brake systems.

Paper A investigates the particle motion inside the pin-on-disc (POD) chamber and eval-

uates the sampling efficiency. The output is used to correct the results in the comparison

between the simulation and experiments in Paper B.

Paper B develops an FEA to evaluate the wear and particle emissions from the disc

brakes, starting from a POD material characterization. The simulation results are compared

with the experimental results performed on a full-scale dyno bench.

Paper C develops an FEA to evaluate the COF of a disc brake, starting from a POD ma-

terial characterization. The simulation results are compared with the experimental results

performed on a full-scale dyno bench.

Paper D develops a CA to investigate the influence of standard cast iron and coated disc

surfaces in the local contact areas.

Paper E extends the CA methodology of Paper D to investigate the influence of the disc

surface roughness of a coated disc on the local contact pressure and contact area.

Paper F develops a multi-scale simulation approach combining FEA, CFD and CA sim-

ulations to investigate the local contact temperature on Cu-full and Cu-free commercial

pads.

vii

Sammanfattning

Luftburna partikelutsläpp från vägfordon är en betydande källorna till dålig luftkvalitet

i städer. Fordonsskivbromsar är en av den största källan till icke-avgasutsläpp som nyligen

visat sig lika stora som avgasutsläpp. I skivbromsar trycks bromsbeläggen mot den

roterande skivan för att bromsa fordonet. Både skivan och beläggen är slits och en del av

slitaget kan bli luftburen. Dessa partiklar kan vara farliga för människors hälsa om de

inandas. Mängden partikelutsläpp från skivbromsar påverkas av en större mängd

kontaktfenomen som t.ex. friktion, slitage, kontakttemperatur, kontakttryck och topografi.

Det är svårt att experimentellt studera vad som händer i kontakten mellan skiva och belägg

under en inbromsning. Dessutom behöver experimenten att friktionsmaterialen och

bromssystemet redan är tillverkat. Syftet med avhandlingen är att utveckla en

simuleringsmetodik för att bättre förstå kontaktfenomen och att utvärdera friktionsmaterial

och bromssystemets tribologiska och emissionsprestanda i den tidiga utvecklingsfasen av

nya bromssystem.

Olika simuleringsmetoder kan användas beroende på vad man vill utvärdera. Ett

makroskopiskt tillvägagångssätt baserat på Finit elementanalys (FEA) kan användas för att

utvärdera slitaget, partikelemissionen och friktionskoefficient (COF) för hela bromssystem.

Ett mesoskopiskt angreppsätt baserat på Cellulära Automater (CA) kan användas för att

utvärdera det lokala kontaktbeteendet mellan skiva och belägg, och påverkan av olika

ingredienser i beläggens friktionsmaterial. Dessa två simuleringsmetoder kan integreras för

att skapa en övergripande simuleringsmetodik som kombinerar flera skalor för att

undersöka och förutsäga kontaktfenomen i bromssystem.

I artikel A undersöks luftburna partiklars rörelse i en box som omsluter en pinne på skiva

tribometer (POD) och utvärderar samplingseffektiviteten. Resultatet används för att

korrigera resultaten då simulerade och uppmätta resultat jämförs i artikel B.

Artikel B beskriver en FEA för att utvärdera slitage och partikelutsläpp från skivbromsar

utifrån materialkarakterisering med tribometer. Simuleringsresultat jämförs med

experimentella resultat som utförs med en fullskalig bromsbänk.

Artikel C beskriver en FEA för att utvärdera COF för en skivbroms med utgångspunkt

från en tribologisk materialkaraktärisering. Simuleringsresultatet jämförs med

experimentella resultat från en bromsbänk.

Artikel D beskriver en CA för att undersöka skillnaden i kontakten mellan en

gjutjärnsskiva och en keramiskt belagd gjutjärnsskiva.

I artikel E utökas CA-metodiken i artikel D för att kunna studera hur keramiskt belagda

bromsskivor kan påverka det lokala kontakttrycket och kontaktarean.

I artikel F utvecklas en flerskalig simuleringsmetodik som kombinerar FEA-, CFD- och

CA-simuleringar för att undersöka den lokala kontakttemperaturen för Cu-fulla och Cu-fria

kommersiella bromsbelägg.

ix

List of appended publications

Paper A A CFD study of a pin-on-disc tribometer setup focusing on airborne par-

ticle sampling efficiency

Published in the conference proceedings of the 6th European COnference on TRIBology 7–9 June

2017, Ljubljana, Slovenia.

Gabriele Riva planned the work, performed the simulation work, evaluated the results and

was responsible for most of the writing.

Paper B An FEA Approach to Simulate Disc Brake Wear and Airborne Particle

Emissions

Published in Tribology International 138 (2019) 90–98.

Gabriele Riva performed part of the simulation work, evaluated the results and was respon-

sible for most of the writing.

Paper C A finite element analysis (FEA) approach to simulate the coefficient of

friction of a brake system starting from material friction characterization

Published in Friction.

Gabriele Riva planned the work, performed part of the simulation work, evaluated the re-

sults, and was responsible for most of the writing.

Paper D A numerical study of disc brakes wear dependence of rotor surface coat-

ing

Published in the conference proceedings of Eurobrake, 22–24 May 2018, The Hague, Netherlands.

Gabriele Riva performed the simulation work, evaluated the results, and was responsible

for most of the writing.

Paper E Simulation of contact area and pressure dependence of initial surface

roughness for cermet-coated discs used in disc brakes

Published in Tribology in Industry Vol. 41, No. 1 (2019) 1–13.

Gabriele Riva planned part of the work, performed the simulation work, evaluated the re-


Paper F A Multi-Scale Simulation Approach to Investigate Local Contact Tem-

peratures for Commercial Cu-Full and Cu-Free Brake Pads

Published in Lubricants 7, 80 (2019).

Gabriele Riva planned the work, performed most of the simulation work, evaluated the re-


x

List of additional publications

Paper G CFD simulation of a meso-combustor with detailed kinetics

Published in the conference proceedings of the XXXVI Meeting of the Italian Section of the Com-

bustion Institute, 13–15 June 2013, Procida, Italy.

Paper H Design, Set-up and Validation of an Aerodynamic Bench for Wheel Cor-

ner Flow Investigation in Vented Brake Disc Testing

Accepted by the conference proceedings of Eurobrake 2020 (accepted on 9 March, 2020).

xiii

Acknowledgements

Most of the presented work has been conducted at the Department of Machine Design at

KTH Royal Institute of Technology in collaboration with Brembo S.p.A. that also funded

this project.

I would like to thank my main supervisor Jens Wahlström to have always been focused on

this project and to have supported me every time I needed. I would like to thank my indus-

trial supervisor Guido Perricone to have always supported and sponsored me in this project.

Thanks also to my Brembo managers Alessandro Ciotti, Raffaello Cornolti and Pietro Barale.

I would like to thank my co-authors and colleagues Mattia Alemani, Matteo Redaelli, Gior-

gio Valota, Giacomo Valsecchi, Francesco Varriale and Fabrizio Venanzoni for the support

to my work during these years.

A special thank goes to my Stockholm friends Pouya, Yang, Nico, Patrick, Abbos, Naveen,

Simo, Elisa, José, Rocco, Benedetta, Bertrand, Gabriel, Bin Bin, Ying Ying, and all the others

I am forgetting. Thank you for the time spent together, I really enjoyed Stockholm with you.

Thanks to my Italian friends Robi, Pago, Emi, Brian, Vincio, Forti, Davide, Albi and Marco.

I would like to thank my mum Maria and my sister Gloria to always support and trust me.

Finally, the biggest thank goes to my girlfriend Valeria, wherever we are I always feel home

with you.

xv

Acronyms

UN: United Nations

CA: Cellular Automaton

CFD: Computational Fluid Dynamic

COF: Coefficient of Friction

Cu: Copper

ELPI: Electrical Low Pressure Impactor

FE: Finite Elements

FEA: Finite Element Analysis

HTC: Heat Transfer Coefficient

LACT: Los Angeles City Traffic

MCA: Movable Cellular Automaton

MD: Molecular Dynamics

PhD: Philosophiae Doctor (Doctor of Philosophy)

PM10: particulate matter 10 micrometres or less in aerodynamic diameter

POD: Pin on Disc

RQ: Research Question

SDG: Sustainable Development Goal

xvii

Contents

1. Introduction ........................................................................................................................1

1.1 Background ................................................................................................................. 2

1.2 Research questions ..................................................................................................... 3

1.3 Thesis outline .............................................................................................................. 4

2. Disc brake systems .............................................................................................................5

2.1 Disc .............................................................................................................................. 5

2.2 Calliper ........................................................................................................................ 6

2.3 Pads ............................................................................................................................. 7

3. Proposed simulation methodology ...................................................................................9

3.1 Pin-on-disc tribometer.............................................................................................. 10

3.2 Dyno .......................................................................................................................... 10

3.3 Finite Element Analysis ........................................................................................... 11

3.4 Thermal CFD simulation ......................................................................................... 13

3.5 CA .............................................................................................................................. 14

4. Summary of results of the appended papers ................................................................. 17

4.1 POD particle sampling efficiency (Paper A)........................................................... 17

4.2 Brake system wear, particle emissions and COF (Paper B and Paper C) ............. 18

4.3 Contact meso-scale results (Paper D, Paper E and Paper F) ................................. 20

5. Discussion, conclusions and future work ....................................................................... 25

5.1 Discussion ................................................................................................................. 25

5.1.1 RQ1 .................................................................................................................... 25

5.1.2 RQ2 .................................................................................................................... 25

5.1.3 RQ3 .................................................................................................................... 28

5.1.4 RQ4 .................................................................................................................... 29

5.2 Conclusions ............................................................................................................... 29

5.3 Future challenges ...................................................................................................... 31

6. Bibliography ..................................................................................................................... 33

Appended papers

xviii

List of Figures

Figure 1: 3D model of a brake system (Paper F). .................................................................. 5

Figure 2: 3D model of a cast iron integral disc. On the left the entire disc; on the right the

disc sectioned in the middle of the ventilation (pillars). ........................................................... 6

Figure 3: 3D model of a fixed aluminium calliper. On the left, the calliper assembly; on

the right, the pads and piston components. .............................................................................. 7

Figure 4: Pad picture. On the left a picture of the entire pad after testing (disc rotation

counter-clockwise). On the right a light optical microscope picture of the friction material.

The red patches are mostly copper fibres; the yellow patches are mostly brass fibres; the blue

patches are mostly steel fibres and the grey/black patches are mostly the homogeneous part

made by the other components described [30]. ......................................................................... 8

Figure 5: Schematic view of the methodology procedure. .................................................. 9

Figure 6: An overview of the inertia dyno bench setup with the important parts marked

(Paper F). .................................................................................................................................... 11

Figure 7: FEA simulation routine. ....................................................................................... 12

Figure 8: CA simulation routine overview (Paper F). ........................................................ 15

Figure 9: Velocity profile at the sampling point (Paper A). ............................................... 17

Figure 10: Simulated mass loss for pads and rotor during one reduced LACT. Left

column: cumulative mass loss. Right column: mass loss per each individual brake event

(Paper B). .................................................................................................................................... 18

Figure 11: Measured (upper row) and simulated (lower row) PM10 emission for brake

event 1–100 of LACT (Paper B). ................................................................................................ 19

Figure 12: COF time history during the selected braking. Experimental COF in black; FEA

COF in red (Paper C). ................................................................................................................ 20

Figure 13: Simulated disc surface topography after braking (Paper D). .......................... 21

Figure 14: Simulated disc surface profile after 3000 seconds. Upper: real disc surface

profile as input. Lower-left: surface profile of the real surface divided by 10. Lower-right:

surface profile of the real surface divided by 100 (Paper E). .................................................. 21

Figure 15: Contact pressure on the pin surfaces. On the left the pin coupled to the coated

disc; on the right the pin coupled to the standard cast iron disc (Paper D). ......................... 22

Figure 16: Simulated contact pressure distribution after 3000 seconds. Upper: real disc

surface profile as input. Lower-left: surface profile of the real surface divided by 10. Lower-

right: surface profile of the real surface divided by 100 (Paper E). ........................................ 22

Figure 17: Simulated contact area. Black: real disc surface profile as input. Blue: surface

profile of the real surface divided by 10. Red: surface profile of the real surface divided by

100 (Paper E). ............................................................................................................................. 23

Figure 18: Pad surface temperature distributions after brake event no. 4 for the Cu-full

and Cu-free materials. Disc rotation counter: clockwise (Paper F). ....................................... 24

xix

List of Tables

Table 1: Isokinetic sampling efficiency. .............................................................................. 17

Table 2: Measured and simulated mass loss after five reduced LACT tests (Paper B). .. 18

Table 3: Measured and simulated airborne PM10 emissions of LACT (Paper B). .......... 19

Introduction | 1

1. Introduction

Low air quality is a problem that affects around 90% of the global population [1]. Conse-

quently, in 2012, air quality improvement has been included in the United Nation’s (UN)

sustainable development goals (SDGs) [2] in order to drive institutions, the scientific com-

munity and companies to focus their attention on this topic. One of the most important pa-

rameters to quantify air quality is the particle concentration. The presence of particles in the

air can affect human health [3]–[5]. Particles emitted from a source can fall to the ground or

adhere to other surfaces, or they can be airborne particles, which can be inhaled by both

humans and animals. Airborne particles in urban areas can come from different sources [6],

such as natural dust and sea salt, industrial activities (e.g. power generation), domestic fuel

combustion and road traffic. Road traffic is actually the primary source of particle emissions

in urban areas [7]. Road traffic emissions are generated from vehicles and can be divided

into two main groups based on the nature of the source: exhaust and non-exhaust emissions.

Exhaust emissions are from vehicle engines and, historically, are the source of all studies.

Recently, non-exhaust emissions have been considered to be as important as engine emis-

sions [8]. Emissions from friction brakes are one of the main sources of non-exhaust emis-

sions from road traffic [9].

Brake emissions are highly dependent on the pad-to-disc contact situation. This means

that all the main phenomena in the sliding contact interface have to be studied, for example,

friction [10], wear [11], contact pressure [12]–[13], contact temperature [14]–[15] and particle

emission [16] itself. The actual approach used by brake manufacturers to design new friction

material is based on experience and trial-and-error processes, in which several formulations

must be produced and several tests performed to evaluate the performance of the friction

material. At the same time, knowing the friction material itself is not enough, because the

same frictional material can show different behaviours if used in different brake systems.

This means that in order to know the performance of an entire brake system, it is necessary

to wait until the system has been manufactured and tested, at least in its prototype form.

Moreover, due to its limited accessibility, it is difficult to fully investigate pad-to-disc con-

tact experimentally in terms of contact pressure, contact area, local wear, local coefficient of

friction (COF), etc. Thus, in this respect, a simulation approach could be beneficial.

The work presented in this thesis deals with the simulation of the contact between disc

and pads in brake systems for commercial vehicles (mainly passenger cars). The develop-

ment of a simulation methodology that is capable of predicting and investigating friction

material and brake system performance not only allows an understanding of the phenom-

ena that are difficult to study through experiments, it also allows the evaluation of the per-

formance of new friction material and new brake systems in the early design phase. This

results in savings in resource consumption in terms of cost and time and a consequential

increase in the sustainability of product development.

Introduction | 2

1.1 Background

From a historical perspective, interest in the contact between pads and disc in brake sys-

tems started with studies based on experimental activities, in which the contact surfaces

were analysed before and after testing. Different kind of tests can be identified according to

the scale of the test and the system involved. Starting from full-scale tests on entire vehicles,

there are road tests [17] in which the brake system is tested with the whole vehicle on roads

or tracks, and chassis dyno tests [18], in which the vehicle is tested in a controlled room with

inertia rolls under the wheels to simulate braking. Always taking into account a full-scale

brake system but without the full-scale vehicle, tests can be performed on a dyno bench or

inertia dynamometer [19]. This is conducted by assembling the disc on a rotating shaft and

the calliper on a fixed support. The dyno bench can be equipped with a clean chamber to

perform tests that focus on particle emissions [20]. Regarding scaled samples, several tribo-

meter systems have been developed. Two main tribometers have been identified: a mini or

scaled dyno [21] and a pin on disc (POD) [22]. Both systems are equipped with a scaled

brake disc and a sample of friction material sliding against the disc. The main difference is

that dynamic braking can be evaluated on a scaled dyno, since the pressure is applied

through a pneumatic system and the disc is assembled on an inertia shaft, while constant

pressure and constant velocity braking can be evaluated on a POD, since the pressure is set

by weights. The issue with physical experiments is that the contact between pads and disc

is not accessible during the test. Thus, the contact behaviour can only be investigated meas-

uring correlated variables such as wear, friction coefficient and particle emissions. The phe-

nomena acting at the interfaces can only be studied a posteriori and it is not possible to eval-

uate what happens in the interface during the contact. Thus, a simulation could help to in-

vestigate the contact behaviour and predict it before testing.

Different kinds of simulation approaches can be used to simulate the pad-to-disc contact

in brake systems, depending on what is to be simulated. The simulation approaches found

in the literature can be divided into two main categories: meso/micro-scale and macro-scale

approaches. Also, a smaller-scale approach, called molecular dynamics, which considers the

interaction between molecules, has been used in the literature, although it will not be the

subject of this work.

The first category is primarily approached using two kinds of simulation: movable cellu-

lar automaton [23]–[25] and cellular automaton [26]–[31]. The movable cellular automaton

method mainly focuses on the simulation of the nanometre third layer, which is formed

during the contact of friction material with the sliding disc. The wear debris detaches from

the two bodies and forms a very thin film (10–100 nm) that is mainly responsible for the

friction properties developed by the contact. The cellular automaton, however, is more fo-

cused on the two contacting bodies interacting with each other, meaning the disc and pad.

Due to the wear from the bodies during contact, some debris that has not been released into

the environment builds up on the original surfaces and modifies the surface topography.

The modification of the two surfaces during contact can be described using some logical

Introduction | 3

rules. In general, the macroscopic wear, friction and particle emission behaviour can be ex-

plained by the formation and destruction of some plateaus, known as secondary plateaus,

on the disc and pad surfaces.

The second category considers the phenomena that mainly act at the macro scale, in

which the design of the brake system components is taken into account and is generally

simulated using finite element analysis (FEA) [32]–[38]. Using this approach, it is possible

to study the macro-contact conditions for a given pad-disc pair. Here, the influence between

different brake systems can also be evaluated. Starting from a tribological characterization

of friction material-disc contact, it is possible to evaluate the wear, friction and particle emis-

sion characteristics of a brake system. In macro-scale approaches, thermal CFD (computa-

tional fluid dynamics) simulation [39]–[42] can also be used to focus on the temperature of

the brake system and study the particle motion inside the test environment.

In the literature, a lack of studies has been identified on the interaction between the two

groups of phenomena and the two groups of simulation. The aim of this thesis is to develop

a simulation procedure capable of making the different scale phenomena interact, starting

from single simulations and then combining them. Moreover, a lack of studies has also been

identified on the virtual characterization of friction material starting from the basic constit-

uents (e.g. fibres, resin). Thus, the aim of the meso-scale simulation also applies to this vir-

tual characterization.

1.2 Research questions

The main objective of this thesis is to develop a simulation methodology to investigate

the performance of the friction materials of a brake system. Performance mainly refers to

friction, wear and particle emission. This main objective can be divided into four main parts.

First, we want to identify the main phenomena that influence the pad-to-disc contact, the

scales involved, and how these different scale phenomena can be simulated. Second, we

study which phenomena can be investigated using the developed methodology. Third, we

compare the simulated and experimental results to verify the simulation validity and to un-

derstand whether the simulation approach can be used to predict observed phenomena.

Lastly, we evaluate how the proposed methodology can impact the sustainable develop-

ment goals.

The objectives described can be summarized in the following research questions (RQs)

that guided the PhD work:

RQ1 How can the sliding contacts in disc brakes be simulated on different size scales to study

tribological effects and airborne emissions?

RQ2 Can simulations be used to explain the system phenomena observed during physical experi-

ments?

Introduction | 4

RQ3 Can simulations be used to predict the tribological and airborne emission performance of disc

brakes?

RQ4 How can the developed simulation methodology impact the sustainable development goals?

1.3 Thesis outline

Chapter 1 starts with a general overview of the work, how this work can be useful – and

its objectives. Chapter 2 introduces disc brake systems in general. Chapter 3 describes the

proposed simulation methodology. Chapter 4 presents the results of the simulation. Chapter

5 discusses the results, the conclusions and presents the next steps for continuing the work.

Disc brake systems | 5

2. Disc brake systems

An automotive brake system is a component of automotive vehicles that has the function

of slowing down a vehicle, keeping a constant speed when going downhill, or keeping the

vehicle steady when parked. Such functions make the brake system a safety-critical compo-

nent of vehicles. A friction brake system transforms the kinetic energy of the vehicle into

frictional heat. Passenger cars can be equipped with two different kinds of friction brake

systems: disc brakes or drum brakes [43]. Nowadays, the better heat dissipation perfor-

mance of disc brake systems has driven car manufacturers to equip their vehicles with these

kinds of brakes, or at least disc brakes on the front, which usually carry most of the load,

and drum brakes on the rear [44]. Recently, electric vehicles have become increasingly pop-

ular. In electric vehicles, part of the standard braking is provided by a regenerative electric

system. These kinds of vehicles are also equipped with standard disc brakes to transform

kinetic energy into heat during all braking conditions in which the regenerative braking

cannot provide a consistent deceleration of the vehicle [45]. For a standard passenger vehicle

equipped with a disc brake system, the braking input is provided by the driver, who de-

presses the brake pedal, or by some active controls (e.g. adaptive cruise control and collision

detection systems). When braking, all the brake fluid inside the system is placed under pres-

sure through a pump. The brake fluid, which is also inside the calliper, pushes one or more

pistons against the pads. The pads, in turn, are pushed against a rotating disc that generates

a tangential force. This tangential force is the braking force and is dependent on the contact

conditions between disc and pads. A model of a brake system is shown in Figure 1.

Figure 1: 3D model of a brake system (Paper F).

2.1 Disc

The disc, which is the rotational part of the brake system, is connected to the wheel axle

by a rigid joint through the bell. This gives the disc the same rotational speed of the wheel.

The bell can be integrated into the disc body and cast together with it. These kinds of discs

are called integral discs. If the bell is attached to the disc by rivets or bolts instead, the disc is


called floating disc. In this kind of disc, the bell is usually manufactured using a different

material.

A third family can be identified when the bell is made of a different material but it is co-cast

with the disc. These are called co-cast discs.

Most discs used in passenger and commercial vehicles are made of cast iron through a

casting process. Sometimes, the brake rings of cast iron discs are coated to increase perfor-

mance. Some expensive and/or performance cars use carbon ceramic brakes in which the

brake disc is made of a ceramic matrix reinforced with carbon fibres. However, carbon ce-

ramic brakes will not be discussed in this work.

Discs commonly used in passenger cars or commercial vehicle are characterized by ven-

tilation between the two brake rings. The ventilation can be made using channels or pillars.

A model of an integral cast iron disc is shown in Figure 2: on the left the entire disc; on

the right the disc sectioned in the middle of the ventilation; in light blue, the pillar section.

Figure 2: 3D model of a cast iron integral disc. On the left the entire disc; on the right the disc sectioned in the middle

of the ventilation (pillars).

2.2 Calliper

The input in terms of pressure provided by the driver is transferred through the hydrau-

lic system to the calliper. As described at the beginning of Chapter 2, when the system is

placed under pressure, the fluid in the calliper pushes one or more pistons that push the

pads against the disc. In a fixed calliper the calliper mainly comprises a calliper body, two or

more pistons, and the pads. In a fixed calliper the calliper body comprises just one part (or

two parts joined together) and there are pistons on both calliper sides and all the pistons are

pushed directly by the fluid against the pads. A floating calliper has two main bodies: a float-

ing calliper body and a carrier. The piston(s) is on just one side of the calliper (piston side).

When the system is placed under pressure, the piston pushes the pad on its side, while the


calliper can slide on two pins and the reaction, which is on the other side (finger side), can

push the other pad. Fixed callipers are generally made of aluminium alloy and are normally

used on more expensive and/or performance vehicles. Floating callipers are usually made

of cast iron. They are less costly and are normally used in commercial vehicles or smaller

cars.

A model of a fixed aluminium calliper is shown in Figure 3. On the left, the calliper as-

sembly is shown; on the right, the pads and piston components are shown.

Figure 3: 3D model of a fixed aluminium calliper. On the left, the calliper assembly; on the right, the pads and piston

components.

2.3 Pads

When the pads slide on the braking ring of the rotating disc, a braking force is generated.

A pad is generally made of a steel backplate and heterogeneous friction material. The piston

pushes the backplate side of the pad while the friction material slides on the disc. Since the

braking force is generated by the contact between the disc and friction material, the compo-

sition of the latter is very important for guaranteeing the performance of the entire brake

system. In general, the friction material used in brake pads comprises a binder, frictional

additives, filler and reinforcing fibres [46]. The binder is made of a polymer-based resin and

holds the components together. Frictional additives control the friction coefficient. Filler is

used to modify certain material properties and keep the material costs low. Fibres carry most

of the load during braking and act as a support for the secondary plateau formation from

compacting wear debris. Fibres are mainly made of metallic materials such as copper, brass

and iron.

In Figure 4 [30] a pad photograph (left) and a light optical microscope picture (right) are

shown. On the left, the pad is a used pad in which the disc rotation is counter-clockwise. On

the right, different patches represent the different components of friction material. The red

patches mainly represent copper fibres; the yellow patches mainly represent brass fibres;

the blue patches mainly represent steel fibres and the grey/black areas mainly represent the


homogenous part of the friction material, which is a mixture of resin, frictional additives

and fillers.

Figure 4: Pad picture. On the left a picture of the entire pad after testing (disc rotation counter-clockwise). On the

right a light optical microscope picture of the friction material. The red patches are mostly copper fibres; the yellow patches

are mostly brass fibres; the blue patches are mostly steel fibres and the grey/black patches are mostly the homogeneous part

made by the other components described [30].

Proposed simulation methodology | 9

3. Proposed simulation methodology

A schematic view of the proposed methodology procedure is shown in Figure 5. First

(box 1), the procedure starts by defining the brake system to be investigated and by defining

the materials, load cycle and environmental conditions. Second (box 2), tribometer tests are

conducted to obtain the input for the simulation such as specific wear, particle emission rate

and local friction coefficient (Paper A, Paper B and Paper C). Third (box 3), dyno bench tests

can be conducted to evaluate brake system wear, particle emissions, friction coefficient and

temperatures (Paper B, Paper C and Paper F). Step two and step three can be carried out in

parallel. Fourth (box 4), the macro contact behaviour of the brake system can be simulated

using an FEA to compute wear, particle emissions and friction coefficient (Paper B, Paper C

and Paper F). Fifth (box 5), the pressure distribution of the FEA can be applied to a thermal

CFD analysis to compute the brake system macro temperatures (Paper F). The results of the

FEA and thermal CFD analysis can be compared with the results of the dyno bench tests.

The contact pressure and temperature results are used as boundary conditions for the last

step (box 6) of the simulation procedure, the CA simulation (Paper D, Paper E and Paper F).

In the CA, the micro contact behaviour is evaluated for both pads and disc. Local wear,

plateau dynamics, local contact pressure and local contact area are simulated. The local con-

tact temperature is also evaluated as a function of the thermal properties of the single com-

ponents of friction material. The results of the CA can also be compared with the results of

the dyno bench tests. In this work, the CA results are only compared with the POD results

as a qualitative verification. However, the aim of the methodology is to validate the whole

simulation with a full-scale test on the dyno bench. All boxes will be explained in detail in

the following sub-section.

Figure 5: Schematic view of the methodology procedure.


3.1 Pin-on-disc tribometer

The friction material and disc material can be tested using a pin-on-disc tribometer, as

conducted by Wahlström et al. [22]. The pin-on-disc tests are performed as described in Pa-

per B. These scaled tests are conducted to obtain a characterization of the friction material

and the disc material in terms of specific wear, local friction coefficient and particle emission

rate. The tests are performed in 12 different conditions and the test results are linearly inter-

polated to obtain three pv maps describing a set of conditions. These maps are used as input

for the FEA simulation described in sub-section 3.3.

Regarding particle emissions, the isokinetic efficiency has been studied in Paper A. This

was carried out to compare the simulation results with the dyno bench test results in which

the facility has been designed to have an isokinetic condition at the sampling point. The

efficiency was evaluated using a two-phase flow analysis performed with the commercial

software StarCCM+ [47]. The particle emission computed by the simulation was corrected

by the POD efficiency to include the effect of anisokinetic sampling.

3.2 Dyno

The dyno bench used is the facility developed by Perricone et al. [20], described in Paper

B, and is shown here in Figure 6. It comprises a clean chamber built inside a dyno bench test

for brake systems. In the dyno bench, the entire brake system was tested with the same

braking load that would have been applied in a road test. The clean chamber was built with

a focus on particle emission measurements. For tests that only focus on friction and wear, a

standard dyno bench without a clean chamber can be used.

The measurement of wear (Paper B) involved weighing the pads and the disc before and

after the test to measure the difference in weight using a Sartorius balance MSE14202S (re-

peatability ±0.01g).

Particle emission measurements (Paper B) were carried out using an ELPI+ (electrical

low pressure impactor). ELPI+ registers the mass concentration at a frequency of 1 Hz. The

PM10 particles were measured, meaning all particles with an aerodynamic diameter of less

than 10 µm.

COF measurement (Paper C) was carried out measuring the normal force with a pressure

sensor and the braking torque with a torque meter. By then dividing the tangential force by

the normal force, it is possible to obtain the COF of the brake system.


Figure 6: An overview of the inertia dyno bench setup with the important parts marked (Paper F).

3.3 Finite Element Analysis

An FEA was performed using the commercial software Abaqus [48] coupled to a user-

developed subroutine. Two different analyses were developed: the first for computing wear

and particle emissions (Paper B) and the second for computing the COF (Paper C). These

two different analyses have been developed because of the different time scale characteris-

tics of the simulated phenomena. The first two phenomena are interesting if observed dur-

ing a complete cycle, since wear and particle emissions do not present relevant results after

just a single braking sequence. However, the COF is also very interesting if studied during

the same braking, to investigate phenomena such as the in-stop growth of the COF, local

hot spots and stability of the COF itself during a braking event. The two different analyses

could be combined in order to have just one FEA capable of computing all the quantities.

Also, because from a process perspective, the two analyses are quite similar, they will be

described here as just one single process. Figure 7 shows the FEA simulation routine.


Figure 7: FEA simulation routine.

The simulation procedure starts with a number of pre-process operations such as definition

of the geometries, mesh and load cycle. Second, an FEA is conducted in order to compute

the contact pressure between pads and disc. In the FEA model, the calliper is fixed with two

constraints corresponding to the fixing points, pressure is applied to the back of the pistons

and against the entire canalization wall, and the disc is put in rotation. All the components

described in Chapter 2 are considered in the simulation. Third, wear, particle emissions and

the COF are computed, taken into account the local conditions of pressure and velocity, in

which local means in every node that is in contact.

Wear computation (Paper B) can be obtained using Archard’s wear law [49]. For the pads,

the wear depth is computed as follows:

( , )p ph k p v p s (1)

where kp is the specific wear rate of the pad obtained by the specific wear map described

in section 3.1, and is a function of pressure and velocity, p is the cell contact pressure, and

Δs is the node sliding distance. Assuming a constant deceleration during braking, the disc

wear can be computed as follows [33]:

2

0

( , ) ( , )

2 2d d

p r p rh k r

(2)


where α is the rotation angle, r and θ are the cylindrical coordinates, and kd is the disc

specific wear rate.

The mass particle emissions for every braking event (Paper B) can be computed starting

with the local pressure and sliding velocity values, as was the case for wear:

1

1

( , )n

nodalparticles POD ELPI i

i pin

Am n p v s

A

(3)

where ηPOD is the particle sampling efficiency of the pin-on-disc tribometer as a result of

anisokinetic sampling, computed in Paper A; nELPI+ is the particle emission per sliding dis-

tance and is given by the pv map; Anodal is the nodal area of the FEA mesh; and Apin is the pin

area.

The brake system COF for every time step (Paper C) can be computed by dividing the tan-

gential force by the normal force:

1

1

2

N

i ci ni

isys p

p Ap A

(4)

where psys is the pressure applied to the brake system; Ap is the piston(s) area; µi is the

local COF obtained by the map mentioned in section 3.1 and is a function of the local contact

pressure and the local sliding velocity; pci is the local contact pressure; and Ani is the nodal

area.

After the wear, particle emission and COF have been computed, the mesh can be updated

and the analysis can be performed for the next braking until the end of the cycle.

3.4 Thermal CFD simulation

Thermal CFD simulation was performed using the commercial software StarCCM+ [47]

(Paper F). The simulation procedure was assisted by two different simulation models: the

first model was a CFD model in which the aerodynamic field was solved to compute the

heat transfer coefficients (HTCs) on the wall of the brake system; the second model was a

thermal model in which the computed HTCs were set as boundary conditions and the tem-

peratures of the brake system were computed.

The CFD model represents the dyno bench described in sub-section 3.2. The Reynolds-

averaged Navier-Stokes (RANS) equations were solved together with the energy equation

and coupled to a k-ε turbulence model [50]. Referring to Figure 6, the mass flow was set at

the inlet and the ambient pressure was set at both the outlets. The rotation was set using a

moving reference frame (MRF) to the disc. The temperature was set on all brake system

components described in section 2 to compute the HTCs. The CFD simulations were run at

different velocities and the HTC maps were linearly interpolated between these different

conditions and represented as a function of velocity.


In the thermal model, all components described in section 2 were simulated. The Fourier

equation [51] was solved to compute the temperature of the brake system. Conduction, con-

vection and radiation between the components were taken into account. For convection, the

HTC distribution obtained by the CFD analysis was mapped on the brake system and line-

arly interpolated as a function of velocity.

3.5 CA

CA is a kind of simulation in which an object is discretized and treated as a set of small

elements, the automata. Every automaton is characterized by a status. The principle of func-

tionality is given by the implementation of logical rules between adjacent automata. These

logical rules are based on what has been observed during the experiments [52]. Moreover,

mechanical equations are computed between different bodies to solve contact and wear, and

thermal equations are also solved in order to find the temperature distribution of the studied

objects. In this thesis, CA methodology has been used to study the formation and destruc-

tion of secondary plateaus on the contact surfaces. Thus, every automaton can change its

status from one that describes the initial surface to secondary plateaus, or return to its orig-

inal status if the secondary plateau is, respectively, created or destroyed on the surface. This

CA simulation procedure has been developed in Paper D, Paper E and Paper F. In Paper D

and Paper E, the simulation approach used by Wahlström [30] to simulate the plateau dy-

namics on the pad surface has been extended to include the plateau dynamics on the disc

surface. In Paper F, the CA has been integrated into a multi-scale procedure to incorporate

the macro boundary conditions of the FEA and thermal CFD simulation. Moreover, the CA

simulation procedure has been extended to compute the temperature inside the friction ma-

terial. The friction material model was also implemented to take into account the different

materials that comprise the friction material mixture. Thus, every single-material compo-

nent modelled has its own thermal properties and the real meso-temperature distribution

on the contact surface can be studied. In Paper F, the disc has been simplified as a flat rigid

surface in order to reduce the computational costs. However, the same approach including

temperature computation can also be extended to the disc. The complete CA simulation

procedure is described below and the CA simulation procedure is shown in Figure 8.


Figure 8: CA simulation routine overview (Paper F).

The simulation starts with a number of pre-process operations such as time and space

discretization, material definition and boundary conditions setting. The boundary condi-

tions are set according to the FEA for the pressure load and to the thermal analysis for the

temperature. The first step of the simulation is to compute the contact condition using a

Winkler’s type elastic foundation model [53]. Having established the local contact pressure,

the second step is to compute the wear according to Archard’s wear law [49]. Third, the

plateau dynamics are simulated using the logical rules implemented in Paper E. Fourth, the

temperature is computed according to the finite difference implementation of the heat trans-

fer equation developed in Paper F. This procedure is repeated for every time step/braking

until the end of the braking cycle.

Summary of results of the appended papers | 17

4. Summary of results of the appended papers

In the following sub-sections, the results are presented. Every sub-section shows the re-

sults referred to a single simulation comprising the overall simulation process described in

section 3-Figure 5: two-phase flow simulation of the POD; FEA to compute brake system

wear, particle emissions and the COF; and meso-scale results from the CA simulation.

4.1 POD particle sampling efficiency (Paper A)

Figure 9 shows the velocity profile at the outlet of the POD chamber (Paper A), which is

the sampling point for airborne particle emissions. As can be seen, the velocity at the outlet

is not parallel to the outlet axis itself. Thus, the unisokinetic particle efficiency will be

proportional to the angle between the probe axis and the velocity vector at this specific

point. The sampling efficiency resulting from the velocity field at the outlet is reported in

Table 1. The efficiency is divided into ultrafine, fine and coarse particles. A confidence

interval has also been added that takes the different velocity angles at different points. The

efficiency results are the same for all the particle sizes considered.

Figure 9: Velocity profile at the sampling point (Paper A).

Table 1: Isokinetic sampling efficiency.

Efficiency % Ultrafine Parti-

cles

Fine Particles Coarse Particles

ηθ 80.8% (±16.5%) 80.8% (±16.5%) 80.8% (±16.5%)


4.2 Brake system wear, particle emissions and COF (Paper B and Paper C)

The mass loss for pads (upper plots) and disc (lower plots) are shown in Figure 10 (Paper

B). On the left, the cumulative mass lost during the cycle is shown and on the right, the wear

for each braking is shown. In Table 2, the simulated and experimental results are compared.

The experimental results comprise the wear resulting from five Los Angeles city traffic

(LACT) cycles. Thus, the simulation results of one cycle are multiplied by a factor of five to

compare the mass that is lost. The simulated total mass lost by the brake system appears to

be perfectly in line with the experimental mass lost measured during the LACT tests, alt-

hough the simulated pad wear has been overestimated and the simulated disc wear under-

estimated by around 20%.

Figure 10: Simulated mass loss for pads and rotor during one reduced LACT. Left column: cumulative mass loss.

Right column: mass loss per each individual brake event (Paper B).

Table 2: Measured and simulated mass loss after five reduced LACT tests (Paper B).

Measured mass loss [g] Simulated mass loss [g] Percentage error [%]

Pads 5.96 7.11 19%

Rotor 4.90 3.94 -19%

Total 10.86 11.05 1%

The measured (upper) and simulated (lower) particle emissions for the first half of the

LACT cycle are shown in Figure 11 (Paper B). During the experimental tests, particle emis-

sions were measured for five LACT cycles and the mean value with a confidence interval is


shown in Figure 11. A comparison between the experimental and simulation results is

shown in Table 3, grouping the braking events into four groups. The results appear to be

qualitatively in line and are generally always within the confidence interval of one standard

deviation, or very close to it.

Figure 11: Measured (upper row) and simulated (lower row) PM10 emission for brake events 1–100 from LACT (Pa-

per B).

Table 3: Measured and simulated airborne PM10 emissions from LACT (Paper B).

Brake event Measured PM10 [mg] Simulated PM10 [mg] Relative error [-]

1–55 74 ± 17 77 4%

56–109 190 ± 47 139 -27%

110–163 106 ± 25 86 -18%

164–217 72 ± 16 68 -6%

1–217 (total) 442 ± 105 370 -16%

Figure 12 (Paper C) shows the friction coefficient during 12 braking events taken from

the LACT cycle, for both the experimental (in black) and simulation (in red) results. The

results show a good correlation between simulation and experiments on the COF develop-

ment during a single braking, although the simulated COF is always larger than the meas-

ured COF.


Figure 12: COF time history during the selected braking events. Experimental COF in black; FEA COF in red (Paper

C).

4.3 Contact meso-scale results (Paper D, Paper E and Paper F)

The CA results represent a portion of the disc and pad surfaces analysed after one or

more braking simulations. The results of the CA allow an analysis of how the contact sur-

faces changed as a result of wear and plateau formation; how these secondary plateaus from

wear debris are distributed; what the real parts of the surface in contact are, and thereby the

real contact pressure distribution and contact area; and the contact temperature distribution,

taking into account the influence of the real contact pressure and the nature of the single

material of the friction mixture in contact. A summary of the main meso-scale results of the

CA obtained in this thesis is presented below.

Figure 13 (Paper D) shows the simulated disc surface topography after a drag test for a

coated disc (left) and a standard cast iron disc (right), respectively. The coated disc still

shows a non-uniform surface topography after the simulated test. This is the combination

of two effects: first, the very low specific wear rate given by the coating to the disc surface

does not allow the surface to wear and become smoother; second, the secondary plateau

formation in the lowlands of the disc surface is not enough to fill all of the gaps. Instead, the

standard cast iron disc shows a band topography with a different surface height at different

radii. This is explained by the surface wear, which also significantly reduces the lowlands

of the disc surface and then the deposition of the secondary plateau itself. Consequently, the

secondary plateaus on the disc surface are actually much higher on the coated disc, which

still has more gaps to fill.


Figure 13: Simulated disc surface topography after braking (Paper D).

Figure 14 (Paper E) shows the disc surface topography after another drag test for a coated

disc using three different levels of initial surface roughness. The surface roughness in the

three cases is the roughness measured through an experimental test, the same roughness

divided by 10 and by 100, respectively. This is carried out in order to evaluate the sensitivity

of the results to the initial surface roughness. As can be seen, the disc with the least rough-

ness is almost completely flat, meaning that the secondary plateaus have completely cov-

ered the lowlands of the disc surface. The other two discs are moving in the same direction,

but they take longer to be filled as the lowlands are deeper and the amount of wear needed

is then higher. This can be translated into a higher running-in time.

Figure 14: Simulated disc surface profile after 3000 seconds. Upper: real disc surface profile as input. Lower-left: sur-

face profile of the real surface divided by 10. Lower-right: surface profile of the real surface divided by 100 (Paper E).

Figure 15 (Paper D) shows the contact pressure distribution on the pins coupled to the

coated disc (left) and the standard cast iron disc (right), respectively. The pin coupled to the

coated disc shows a less uniform contact pressure distribution and therefore higher contact

pressure peaks. Whereas, the pin coupled to the standard cast iron disc shows a more uni-

form contact pressure distribution. This is because the disc wear rate is much higher on the

standard cast iron disc, which allows the disc surface to match up with the pin surface. In

Figure 16 (Paper E), the pin contact pressure is shown for three different pins: the first pin

is the pin coupled to the coated disc, which has a roughness equal to the roughness meas-

ured (upper); the second pin is the pin coupled to the coated disc, which has a surface rough-

ness 10 times lower (lower-left); and the third pin is the pin coupled to the coated disc, which


has a surface roughness 100 times lower (lower-right). The contact pressure is proportional

to the roughness: the higher the roughness, the higher the peaks of contact pressure, and the

contact pressure itself is less uniformly distributed.

Figure 15: Contact pressure on the pin surfaces. On the left the pin coupled to the coated disc; on the right the pin

coupled to the standard cast iron disc (Paper D).

Figure 16: Simulated contact pressure distribution after 3000 seconds. Upper: real disc surface profile as input.

Lower-left: surface profile of the real surface divided by 10. Lower-right: surface profile of the real surface divided by 100

(Paper E).


The contact pressure differences result in different behaviour in a contact area, shown in

Figure 17 (Paper E). A more uniform contact pressure directly results in a larger contact

area, the normal load being the same in all the configurations. It is also possible to see how

a lower surface roughness results in a shorter running-in time. In fact, the smoothest disc

surface reaches a steady condition after around 100 seconds of simulation, while the other

two surfaces are still running-in after 3000 seconds.

Figure 17: Simulated contact area. Black: real disc surface profile as input. Blue: surface profile of the real surface di-

vided by 10. Red: surface profile of the real surface divided by 100 (Paper E).

Contact pressure peaks can cause hot spots on the pad surface. These hot spots are also

influenced by the local fibre material, which carries most of the contact together with the

formed secondary plateaus. Taking into account the different thermal properties of different

pad materials, it is possible to study the effects of friction material composition on the con-

tact temperature. In Figure 18 (Paper F), two different friction materials, one Cu-full (upper)

and one Cu-free (lower), are compared under the same braking conditions. The results show

higher peaks of temperature on the Cu-full material due to the lower thermal diffusivity of

the homogenous part of the friction material. The heat is mainly generated on the fibres and

secondary plateaus where most of the load is carried and is then propagated towards the

other areas of the pad. Since the diffusivity of the Cu-full material is lower (Paper F – Table

6), the heat finds a higher resistance at which to be propagated and this results in higher

temperature peaks in the Cu-full material.


Figure 18: Pad surface temperature distributions after brake event no. 4 for the Cu-full and Cu-free materials. Disc

rotation counter: clockwise (Paper F).

Discussion, conclusions and future work | 25

5. Discussion, conclusions and future work

5.1 Discussion

The results shown in section 4 are a summary of the main outcomes of the simulation

procedure developed during this PhD. These results are discussed below according to the

research questions presented in sub-section 1.2.

5.1.1 RQ1

How can the sliding contacts in disc brakes be simulated on different size scales to study tribolog-

ical effects and airborne emissions?

The sliding contacts in disc brakes can be simulated by dividing the phenomena into two

main groups: macro-scale phenomena, in which the characteristic length is in the order of

the brake system size (mm), and meso-scale phenomena, in which the characteristic length

is in the order of µm, typical of the single components of friction material. Thus, the macro-

scale results focus on the entire brake system and are mainly obtained using an FEA. The

meso-scale results mainly focus on the friction and disc surface and composition, and are

obtained using a CA approach. Moreover, the results of airborne particle investigation in

the POD chamber have been also shown at the beginning. These results are useful for sup-

porting an FEA in particle emission computation. The two different scale simulation ap-

proaches are interdependent and can be coupled, as explained in section 3. The results from

the FEA in terms of pressure distribution and the results from the thermal CFD analysis in

terms of pad temperature distribution can be used as boundary conditions in the CA anal-

ysis to study the mesoscopic contact conditions in a real operational brake system environ-

ment.

5.1.2 RQ2

Can simulations be used to explain system phenomena observed during experiments?

The macro results from the FE simulations can be used to describe three main physical

phenomena: wear (Figure 10 – Paper B), particle emissions (Figure 11 – Paper B) and friction

coefficient (Figure 12 – Paper C). The computed wear provides a description of how the disc

and pad surfaces are modified during braking and how the contact situation changes from

one braking to another. Particle emissions are a consequence of wear, since wear debris can

be released into the environment, forming an aerosol with the air. These particles can prop-

agate in the environment and can be harmful to human health. The third main phenomenon

identified is the friction coefficient developed in the sliding pad-to-disc contact that deter-

mines the brake system’s performance. The study of the COF allows some phenomena to be

investigated such as the in-stop increase or decrease in the COF. All these phenomena de-

pend on the local pad-to-disc contact conditions. In the FEA, these local conditions are taken

into account using as input wear, particle emission rate and friction maps (see sub-section

3.1).


In the literature ([32] and [34]), a similar FEA has been used to simulate wear and air-

borne emissions, simplifying the model without considering the calliper. This method is

adopted to reduce the required computational effort. This method could work if the brake

system being considered has quite a uniform contact pressure and the calliper does not in-

fluence the way in which the pads press against the disc. Introducing the calliper, instead,

allows this effect to be considered and also a comparison to be made of the geometries of

different brake systems and their impact on wear and emissions. Valota et al. [33] introduced

the calliper in a similar model, without considering the contact condition dependence of the

local contact pressure and sliding velocity. Again, this does not allow a full comparison of

two different brake systems to be made using different materials because the wear depend-

ence of the contact pressure and sliding velocity is only considered in Archard’s wear law

(Eq. 1) in terms of the pressure and the sliding distance, but not implicitly in the specific

wear rate.

The increase in the COF is visible in Figure 12 and is usually verified during the running-

in process of every single braking sequence. The decrease in the COF can be explained by

considering the temperature effects on the friction material, which can result in fading con-

ditions in the friction material itself and then a decrease in the COF. This can be compared

to what is shown in [30]. A similar increase in the COF is seen at the beginning of the brak-

ing. Following this, in [30] it is possible to see a stabilization of the COF. This can be ex-

plained by considering the energy of the applied braking, since higher energy braking re-

sults in a shorter running-in time. In the experimental results it is possible to see a decrease

in the COF. This can be explained by the fact that the temperature continues to increase and

some fading effects can cause a decrease in the COF. By evaluating the local COF on the pad

surface, it is possible to identify the area in which the COF is higher. Consequently, the

higher power that is generated results in a higher temperature and therefore possible fading

effects. Extending the methodology and the COF map (Paper C) to also consider the tem-

perature variable would allow these phenomena to be better represented in the simulation

model. The extension of the methodology to include temperature can be carried out by de-

veloping a dynamic FE model in which the heat is generated directly at the interface accord-

ing to the local COF obtained by extended maps. Although this model could achieve more

accurate results in terms of COF estimation, it has to be considered that during an urban

traffic cycle, which is the most common way of using a brake system, high temperatures

occur just on the friction material and disc. The heat generation is usually not sufficient to

heat up all the other components (e.g. calliper body), where it can be considered reasonable

to neglect the thermo-elastic effects during a city traffic load cycle. Instead, the thermo-elas-

tic effects on the entire brake system can be important when studying high energy braking

load cycles. Also, dynamics and instabilities should be taken into account if the focus is on

NVH phenomena. It is important to note that the COF computation approach developed

here can be directly transferred to different FEA that focus on thermo-elastic effects and/or

NVH phenomena.

Macro phenomena are also correlated with the mesoscale phenomena discussed in Paper

D, Paper E and Paper F. Wear on the mesoscale is computed in the same way as wear on the


macroscale and it affects the surface topography (Figure 13 and Figure 14). The plateau dy-

namics, together with the wear, also affect the surface topography on the mesoscale. The

higher formation of secondary plateaus on the surface of the coated disc [57] can be ex-

plained by the low specific wear rate resulting from the coating. Due to very low specific

wear, the coated disc does not significantly modify its surface, keeping the lowlands on

which the secondary plateaus can be formed (Figure 13). However, the standard cast iron

disc surface wears, becomes more uniform and does not allow the secondary plateaus to

deposit consistently. Also, the roughness of the coated disc surface results in different sur-

face topographies after testing (Figure 14) that modify the pressure distributions (Figure 15)

and the different contact area levels (Figure 17). The different levels of roughness result in a

different COF [58]: lower disc roughness shows a higher COF. Taking into account the nano-

sized thick tribofilm [59] formed between the contact surfaces, the COF is lower at higher

pressure, since it is easier for this third layer to shear, as discussed by Österle et al. [60]. In

this way, the results of the work on contact pressure and contact area presented in this thesis

could be used to explain the influence of disc surface roughness level on the COF. The COF

could also be investigated by considering the influence of every single component of the

friction material, as was the case in Paper F for the local contact temperature. In fact, the

local friction coefficient together with the local thermal properties of a specific material, and

the local pressure and sliding velocity conditions, could influence the local temperature dis-

tribution. The local contact temperature (Paper F – Figure 18) can then influence all the pre-

viously described phenomena, since all the variables involved are temperature dependent.

Then, if the mechanical properties are known as a function of temperature, the thermo-elas-

tic effects can also be taken into account. The single components of friction material and the

disc surface can be subjected to thermal expansion and/or thermal softening, modifying the

contact situation. Due to different stiffness values at different temperatures, the gaps be-

tween the surfaces can change affecting the development of secondary plateaus. Moreover,

softening of fibre and secondary plateau stiffness at high temperatures could result in more

uniform pressure distribution. In turn, this more uniform pressure distribution could influ-

ence the contact temperature distribution itself (Figure 18). In addition, the heat partition

between disc and pads could be also affected by the temperature and the status of the con-

tact bodies. Here, for the sake of simplicity, the formula proposed by Vernotte [61], which

considers the surfaces and the thermal properties of the two components in contact, has

been used. Extending Vernotte’s approach, the temperature of the surfaces in contact and a

contact resistance that simulates the third layer can also be considered. This heat partition

choice can influence the surface contact temperature and, consequently, all the phenomena

described above [62]. Taking all these effects into account could help identify, for example,

where fading effects occur and how the single components of friction material influence

them or explain high local wear.


5.1.3 RQ3

Can simulations be used to predict the tribological and airborne emission performance of disc

brakes?

The simulation results have been compared with the experimental results to investigate

the validity of the simulation. The validity of the simulation approach can allow future pre-

dictions of the tribological and airborne performance.

Starting from the entire brake system results from the FEA, Table 2 reports the experi-

mental and simulation mass lost during an LACT cycle for both pads and disc (rotor). It

should be noted that in the test, the mass lost has been computed by weighing the compo-

nents both before and after five repetitions of the test, while in the simulation, one test was

performed and the mass lost has been multiplied by a factor of five. The total simulated

wear appears to be fully in line with the experimental wear measured, even if the pad wear

has been overestimated and the disc wear underestimated. Figure 11 and Table 3 show the

comparison between measured and simulated emissions. The breaking emissions in the his-

togram comparison and the sum of the group of emissions reported in Table 3 suggest that

the simulation results are qualitatively in line with the experimental measures. Figure 12

shows the comparison of the COF between the experimental and the simulation results. The

simulated COF appears to be fully aligned with the experimental COF regarding the devel-

opment during a single braking, representing the in-stop increase in COF for every simu-

lated braking event. However, there is a positive offset of the simulated COF which is not

constant for every braking event.

Regarding the mesoscopic results of the CA simulation, there is no explicit validation of

the results of this work, although there are some comparisons with experimental results

from the literature. The comparison of a standard cast iron disc and a coated disc surface

simulated in Paper D appears to be qualitatively in line with the POD experiments per-

formed by Lyu et al. [57]. As mentioned in sub-sub-section 5.1.2, the disc surface of the

standard cast iron disc is smoother and has circumferential bands, while the coated disc

surface appears to be less uniform. The same applies to the pins, in which the pin coupled

to the standard cast iron disc has a more uniform surface compared to the pin coupled to

the coated disc, which can be translated into the higher contact pressure distribution of the

second pin shown in Figure 15. Also, the influence of the surface roughness (Paper E) on the

coated disc presented in this thesis is qualitatively in line with what has been presented by

Federici et al. [58]. Lower surface roughness results in a higher COF, which can be consid-

ered to be in line with the higher contact area of Figure 17, as mentioned in sub-sub-section

5.1.2. In general, we can say that the results from the CA appear to be qualitatively in line

with the experimental results and move in the same direction. However, more comprehen-

sive tests are needed in the future. As mentioned in 3 (Figure 5), the idea is to validate the

CA results directly using full scale dyno tests.


5.1.4 RQ4

How can the developed simulation methodology impact the sustainable development goals?

In 2015, world leaders agreed to identify 17 common goals [2] focusing on the future

order to create a more sustainable world for everyone. Every strategy and/or research pro-

ject should take into account these goals. Below is an explanation of how this work can im-

pact some of these goals.

The first goal affected by the present work is SDG3: “Good health and well-being”. The

specific target in focus is 3.9: “By 2030, substantially reduce the number of deaths and ill-

nesses from hazardous chemicals and air, water and soil pollution and contamination.” As

described in the introduction, urban air quality is affected by particle emissions. Brakes are

one of the main causes of non-exhaust particle emissions. Particle emissions are affected by

all the contact phenomena. Thus, a methodology to simulate these phenomena could help

to better understand particle emissions, develop brake systems with particle emission stand-

ards, and then move forwards towards improving air quality.

The second goal affected by the present work is SDG9: “Industry, innovation and infra-

structure”. The specific target in focus is 9.5: “Enhance scientific research, upgrade the tech-

nological capabilities of industrial sectors in all countries, in particular developing countries,

including, by 2030, encouraging innovation and substantially increasing the number of re-

search and development workers per 1 million people and public and private research and

development spending”. The aim of this work is to investigate and predict brake system

performance affected by contact phenomena in order to innovate brake system technology.

At the same time, the phenomena object of this study are still not 100% clear. Thus, further

research on this topic could improve the understanding of sliding contact physics.

The third and final goal affected by the present work is SDG11: “Sustainable cities and

communities”. The specific target in focus is 11.6: “By 2030, reduce the adverse per capita

environmental impact of cities, including by paying special attention to air quality and mu-

nicipal and other waste management”. This is related to the first target discussed here. Brake

system emissions primarily affect urban air quality. Thus, studying these phenomena can

reduce the environmental impact in cities in terms of higher air quality.

5.2 Conclusions

A simulation procedure comprising different simulation scales and different analyses has

been developed to study the friction material, disc and tribological and emission perfor-

mance of the entire brake system. Two main approaches have been used: an FEA, which

focuses on macro-scale phenomena, and a CA simulation, which focuses on meso-scale phe-

nomena. These two main simulation approaches have not only been shown to simulate the

phenomena of different scales but have also been combined together to establish an overall

simulation procedure. This new proposed methodology is capable of studying the main

contact phenomena such as wear, particle emissions, COF, surface topography and plateau


dynamics, local contact pressure, real contact area and local contact temperature. The simu-

lation results have also been compared with the experimental results to evaluate the validity

of the proposed approach. A results comparison suggests that the approach is promising

and can be useful for studying and predicting brake performance in the very early design

phase, and for studying friction material before its final formulation has been produced. The

answers to the research questions are summarized below.

RQ1 How can the sliding contacts in disc brakes be simulated on different size scales to study

tribology and airborne emission?

The sliding contact in disc brakes can be simulated using an FEA to evaluate the

macro performance of the brake system and a CA approach to investigate the meso

performance of the friction material. Brake system wear, emissions and COF perfor-

mance can be evaluated using an FEA approach that starts from the local character-

ization of the friction material-to-disc contact. The local characterization is intended

to be a map of specific wear rate, specific emission rate and a COF as a function of

local pressure and sliding velocity conditions, respectively. These maps that de-

scribe the local conditions are obtained through POD tests. The pad-to-disc local

contact behaviour in terms of surface topography evolution, secondary plateau dy-

namics, local contact pressure, local contact area and fibre material influence on the

local contact temperature can be evaluated using a CA approach. This approach can

be also integrated into a multi-scale simulation procedure, in which the macro-scale

results can be used as boundary conditions.

RQ2 Can simulations be used to explain system phenomena observed during experiments?

The developed simulation procedure can explain phenomena observed during ex-

periments. Non-uniform wear can be studied by analysing the wear distribution

from the FEA analysis, as well as the dependency of the emissions on the braking

conditions. The increase in the in-stop COF can also be studied through the FEA

analysis. The different running-in times starting from the different disc surfaces, in

terms of coated or standard cast iron and in terms of surface roughness, can be ex-

plained using the CA. Phenomena affecting the performance of a disc-pad pair, such

as fading effects, can be evaluated by analysing the local contact pressure and the

local contact temperature distribution. How the local temperature distribution is af-

fected by the fibre materials can also be taken into account.

RQ3 Can simulations be used to predict the tribological and airborne emission performance of disc

brakes?

The simulation can be used to predict the tribological and airborne emission perfor-

mance of disc brakes. FEA results have been directly compared with dyno bench

results in which the entire brake system has been tested. The comparison shows a

qualitatively good correlation for wear, emissions and COF. The performance of the

brake system can then be predicted if the material characterization from the POD is

available. In such cases, no tests of the entire brake system would be needed a priori

to run the simulation. Some comparisons between CA simulation and POD tests


show a qualitative correlation. Using the presented methodology, the influence of

the fibre materials on the contact temperature can already be predicted. Other types

of performance, depending on the composition of the friction material can be pre-

dicted if a characterization of the single components is made. In general, notwith-

standing the good correlation shown, more tests are needed to confirm the reliability

of the results and to use the methodology as a virtual validation tool.

RQ4 How can the developed simulation methodology impact the sustainable development goals?

The developed methodology mainly affects three sustainable development goals.

The first goal affected is SDG3, since the study of particle emissions can help im-

prove the air quality and, consequently, the health of people and animals. The sec-

ond goal affected is SDG9, since this work studies the physics of contact phenomena

that are still not clear, and support the development of innovative brake systems.

The last main goal to be affected is SDG11, which is related to the first goal here

mentioned. Brake emissions mainly affect the air quality in urban areas, thus, if

greener brake systems are produced, they will contribute to developing more sus-

tainable cities.

5.3 Future challenges

The results of this PhD work may be interesting to both the scientific community and to

industrial partners. The research group has several future steps in mind, which can be de-

scribed as follows:

- Implement test procedures to characterize the friction material as described in sub-

section 3.1 to also include temperature as a variable in addition to contact pressure

and sliding velocity. The FEA can then also be extended to take into account the brake

system temperature computation. This could enable better investigation of the phe-

nomena, e.g. in-stop temperature increase and fading effects.

- In the CA simulation, some single components of the friction mixture have been mod-

elled in order to consider their influence on the contact temperature. The thermo-

mechanical properties of single materials could also be taken into account in the con-

tact model. Some nano-tribometer tests could then be performed to evaluate the

thermo-mechanical properties of these single components. In this way, the thermo-

mechanical effects on the local pressure and temperature distribution can be consid-

ered.

- In the CA simulation, the COF computation could be implemented to identify the

contribution of every single component of the friction material mixture. To achieve

this, a friction characterization of the single components must be carried out. In this

respect, tests on tribometer (POD, mini-dyno or nano-tribometer) must be designed

and performed. In this way, different friction materials can be compared in terms of

their friction performance before their final formulation is realized.


- The same approach in the previous bullet point can be used for wear, identifying the

contribution made by the single components of the friction material being modelled.

This would enable a comparison to be made of the wear performance of the different

friction materials before their final formulation is realized.

- The third layer influence on tribological and emission performance must be further

investigated, e.g. using simulation techniques such as movable cellular automaton

(MCA) and molecular dynamics (MD).

- All the simulation approaches developed can be combined to realize an out-of-the-

box tool ready for use.

Bibliography | 33

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a methodology to simulate automotive disc brake tribology

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