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An adhesion railway relies on adhesion traction to move the train, and is the most widespread and common type of railway in the world. Adhesion traction is the friction between the drive wheels and the steel rail. Since the vast majority of railways are adhesion railways, the term adhesion railway is used only when it is necessary to distinguish adhesion railways from railways moved by other means, such as by a stationary engine pulling on a cable attached to the cars or by a pinion meshing with a rack.

The friction between the wheels and rails occurs in the wheel–rail interface or contact patch. The traction force, the braking forces and the centering forces all contribute to stable running. However, running friction increases costs, due to higher fuel consumption and increased maintenance needed to address fatigue damage and wear on rail heads and on the wheel rims and rail movement from traction and braking forces.

Variation of friction coefficient

Traction or friction is reduced when the top of the rail is wet or frosty or contaminated with grease, oil or decomposing leaves which compact into a hard slippery lignin coating. Leaf contamination can be removed by applying "Sandite" (a gel–sand mix) from maintenance trains, using scrubbers and water jets, and can be reduced with long-term management of railside vegetation. Locomotives and trams use sand to improve traction when driving wheels start to slip.

Effect of adhesion limits

Adhesion is caused by friction, with maximum tangential force produced by a driving wheel before slipping given by:

${\displaystyle F_{\mathrm {max} }=\mu W,}$

where ${\displaystyle \mu }$ is the coefficient of friction and ${\displaystyle W}$ is the weight on the wheel.

Usually the force needed to start sliding is greater than that needed to continue sliding. The former is concerned with static friction (also known as "stiction") or "limiting friction", whilst the latter is dynamic friction, also called "sliding friction".

For steel on steel, the coefficient of friction can be as high as 0.78, under laboratory conditions, but typically on railways it is between 0.35 and 0.5, whilst under extreme conditions it can fall to as low as 0.05. Thus a 100-tonne locomotive could have a tractive effort of 350 kilonewtons, under the ideal conditions (assuming sufficient force can be produced by the engine), falling to 50 kilonewtons under the worst conditions.

Steam locomotives suffer particularly badly from adhesion issues because the traction force at the wheel rim fluctuates (especially in 2- or most 4-cylinder engines) and, on large locomotives, not all wheels are driven. The "factor of adhesion", being the weight on the driven wheels divided by the theoretical starting tractive effort, was generally designed to have a value of 4 or slightly higher, reflecting a typical wheel–rail friction coefficient of 0.25. A locomotive with a factor of adhesion much lower than 4 would be highly prone to wheelslip, although some 3-cylinder locomotives, such as the SR V Schools class, operated with a factor of adhesion below 4 because the traction force at the wheel rim does not fluctuate as much. Other factors affecting the likelihood of wheelslip include wheel size, the sensitivity of the regulator and the skill of the driver.

All-weather adhesion

The term all-weather adhesion is usually used in North America, and refers to the adhesion available during traction mode with 99% reliability in all weather conditions.

Toppling conditions

The maximum speed at which a train can proceed around a turn is limited by the radius of turn, the position of the centre of mass of the units, the wheel gauge and whether the track is superelevated, or canted.

Toppling will occur when the overturning moment due to the side force (centrifugal acceleration) is sufficient to cause the inner wheel to begin to lift off the rail. This may result in loss of adhesion – causing the train to slow, preventing toppling. Alternatively, the inertia may be sufficient to cause the train to continue to move at speed, causing carriages to topple completely.

For a wheel gauge of 1.5 m (4.9 ft) with no canting, a centre of gravity height of 3 m (9.8 ft) and a speed of 30 m/s (110 km/h; 67 mph), the minimum radius of curvature is 360 m (1,180 ft). For a modern, exceptionally high-speed train at 80 m/s (290 km/h; 180 mph), the minimum radius would be about 2.5 km (1.6 mi). In practice, the minimum radius of turn is much greater than this, as contact between the wheel flanges and rail at high speed could cause significant damage to both. For very high speeds, the minimum adhesion limit again appears appropriate, implying a radius of turn of about 13 km (8.1 mi). In practice, curved tracks used for high speed travel are superelevated or canted, so that the minimum radius of curvature is closer to 7 km (4.3 mi).

During the 19th century, it was widely believed that coupling the drive wheels would compromise performance, and this was avoided on engines intended for express passenger service. With a single drive wheelset, the Hertzian contact stress between the wheel and rail necessitated the largest-diameter wheels that could be accommodated. The weight of locomotives was restricted by the stress on the rail, and sandboxes were required, even under reasonable adhesion conditions.

Directional stability and hunting instability

It may be thought that the wheels are kept on the tracks by the flanges. However, close examination of a typical railway wheel reveals that the tread is burnished but the flange is not—the flanges rarely make contact with the rail and, when they do, most of the contact is sliding. The rubbing of a flange on the track dissipates large amounts of energy, mainly as heat but also including noise and, if sustained, would lead to excessive wheel wear.

Centering is actually accomplished through shaping of the wheel. The tread of the wheel is slightly tapered. When the train is in the centre of the track, the region of the wheels in contact with the rail traces out a circle which has the same diameter for both wheels. The velocities of the two wheels are equal, so the train moves in a straight line.

If, however, the wheelset is displaced to one side, the diameters of the regions of contact, and hence the tangential velocities of the wheels at the running surfaces, are different and the wheelset tends to steer back towards the centre. Also, when the train encounters an unbanked turn, the wheelset displaces laterally slightly, so that the outer wheel tread speeds up linearly, and the inner wheel tread slows down, causing the train to turn the corner. Some railway systems employ a flat wheel and track profile, relying on cant alone to reduce or eliminate flange contact.

Understanding how the train stays on the track, it becomes evident why Victorian locomotive engineers were averse to coupling wheelsets. This simple coning action is possible only with wheelsets where each can have some free motion about its vertical axis. If wheelsets are rigidly coupled together, this motion is restricted, so that coupling the wheels would be expected to introduce sliding, resulting in increased rolling losses. This problem was alleviated to a great extent by ensuring that the diameters of all coupled wheels were very closely matched.

With perfect rolling contact between the wheel and rail, this coning behaviour manifests itself as a swaying of the train from side to side. In practice, the swaying is damped out below a critical speed, but is amplified by the forward motion of the train above the critical speed. This lateral swaying is known as hunting oscillation. Hunting oscillation was known by the end of the 19th century, although the cause was not fully understood until the 1920s, and measures to eliminate it were not taken until the late 1960s. The maximum speed was limited not by raw power but by a possible instability in the motion.

The kinematic description of the motion of tapered treads on the two rails is insufficient to describe hunting well enough to predict the critical speed. It is necessary to deal with the forces involved. There are two features which must be taken into account:

1. the inertia of the wheelsets and vehicle bodies, giving rise to forces proportional to acceleration;
2. the distortion of the wheel and track at the point of contact, giving rise to elastic forces.

The kinematic approximation corresponds to the case which is dominated by contact forces.

An analysis of the kinematics of the coning action yields an estimate of the wavelength of the lateral oscillation:

${\displaystyle \lambda ={2\pi }{\sqrt {\frac {rd}{2k}}},}$

where d is the wheel gauge, r is the nominal wheel radius and k is the taper of the treads. For a given speed, the longer the wavelength and the lower the inertial forces will be, so the more likely it is that the oscillation will be damped out. Since the wavelength increases with reducing taper, increasing the critical speed requires the taper to be reduced, which implies a large minimum radius of turn.

A more complete analysis, taking account of the actual forces acting, yields the following result for the critical speed of a wheelset:

${\displaystyle V^{2}={\frac {Wrad^{2}}{k\left(4C+md^{2}\right)}},}$

where W is the axle load for the wheelset, a is a shape factor related to the amount of wear on the wheel and rail, C is the moment of inertia of the wheelset perpendicular to the axle, m is the wheelset mass.

The result is consistent with the kinematic result in that the critical speed depends inversely on the taper. It also implies that the weight of the rotating mass should be minimised compared with the weight of the vehicle. The wheel gauge appears in both the numerator and denominator, implying that it has only a second-order effect on the critical speed.

The true situation is much more complicated, as the response of the vehicle suspension must be taken into account. Restraining springs, opposing the yaw motion of the wheelset, and similar restraints on bogies, may be used to raise the critical speed further. However, in order to achieve the highest speeds without encountering instability, a significant reduction in wheel taper is necessary. For example, taper on Shinkansen wheel treads was reduced to 1:40 (when the Shinkansen first ran) for both stability at high speeds and performance on curves. That said, from the 1980s onwards, the Shinkansen engineers developed an effective taper of 1:16 by tapering the wheel with multiple arcs, so that the wheel could work effectively both at high speed as well as at sharper curves.

Forces on wheels, creep

The behaviour of vehicles moving on adhesion railways is determined by the forces arising between two surfaces in contact. This may appear trivially simple from a superficial glance but it becomes extremely complex when studied to the depth necessary to predict useful results.

The first error to address is the assumption that wheels are round. A glance at the tyres of a parked car will immediately show that this is not true: the region in contact with the road is noticeably flattened, so that the wheel and road conform to each other over a region of contact. If this were not the case, the contact stress of a load being transferred through a line contact would be infinite. Rails and railway wheels are much stiffer than pneumatic tyres and tarmac but the same distortion takes place at the region of contact. Typically, the area of contact is elliptical, of the order of 15 mm across.

The distortion in the wheel and rail is small and localised but the forces which arise from it are large. In addition to the distortion due to the weight, both wheel and rail distort when braking and accelerating forces are applied and when the vehicle is subjected to side forces. These tangential forces cause distortion in the region where they first come into contact, followed by a region of slippage. The net result is that, during traction, the wheel does not advance as far as would be expected from rolling contact but, during braking, it advances further. This mix of elastic distortion and local slipping is known as "creep" (not to be confused with the creep of materials under constant load). The definition of creep in this context is:

${\displaystyle {\mbox{creep}}={\frac {({\mbox{actual displacement}}-{\mbox{rolling displacement}})}{({\mbox{rolling displacement}})}}\,}$

In analysing the dynamics of wheelsets and complete rail vehicles, the contact forces can be treated as linearly dependent on the creep (Joost Jacques Kalker's linear theory, valid for small creepage) or more advanced theories can be used from frictional contact mechanics.

The forces which result in directional stability, propulsion and braking may all be traced to creep. It is present in a single wheelset and will accommodate the slight kinematic incompatibility introduced by coupling wheelsets together, without causing gross slippage, as was once feared.

Provided the radius of turn is sufficiently great (as should be expected for express passenger services), two or three linked wheelsets should not present a problem. However, 10 drive wheels (5 main wheelsets) are usually associated with heavy freight locomotives.

Getting the train moving

The adhesion railway relies on a combination of friction and weight to start a train. The heaviest trains require the highest friction and the heaviest locomotive. The friction can vary a great deal, but it was known on early railways that sand helped, and it is still used today, even on locomotives with modern traction controls. To start the heaviest trains, the locomotive must be as heavy as can be tolerated by the bridges along the route and the track itself. The weight of the locomotive must be shared equally by the wheels that are driven, with no weight transfer as the starting force builds. The wheels must turn with a steady driving force on the very small contact area of about 1 cm between each wheel and the top of the rail. The top of the rail must be dry, with no man-made or weather-related contamination, such as oil or rain. Friction-enhancing sand or an equivalent is needed. The driving wheels must turn faster than the locomotive is moving (known as creep control) to generate the maximum coefficient of friction, and the axles must be driven independently with their own controller because different axles will see different conditions. The maximum available friction occurs when the wheels are slipping/creeping. If contamination is unavoidable the wheels must be driven with more creep because, although friction is lowered with contamination, the maximum obtainable under those conditions occurs at greater values of creep. The controllers must respond to different friction conditions along the track.

Some of the starting requirements were a challenge for steam locomotive designers – "sanding systems that did not work, controls that were inconvenient to operate, lubrication that spewed oil everywhere, drains that wetted the rails, and so on.." Others had to wait for modern electric transmissions on diesel and electric locomotives.

The frictional force on the rails and the amount of wheel slip drops steadily as the train picks up speed.

A driven wheel does not roll freely but turns faster than the corresponding locomotive velocity. The difference between the two is known as the "slip velocity". "Slip" is the "slip velocity" compared to the "vehicle velocity". When a wheel rolls freely along the rail the contact patch is in what is known as a "stick" condition. If the wheel is driven or braked the proportion of the contact patch with the "stick" condition gets smaller and a gradually increasing proportion is in what is known as a "slip condition". This diminishing "stick" area and increasing "slip" area supports a gradual increase in the traction or braking torque that can be sustained as the force at the wheel rim increases until the whole area is "slip". The "slip" area provides the traction. During the transition from the "all-stick" no-torque to the "all-slip" condition the wheel has had a gradual increase in slip, also known as creep and creepage. High adhesion locomotives control wheel creep to give maximum effort when starting and pulling a heavy train slowly.

Slip is the additional speed that the wheel has and creep is the slip level divided by the locomotive speed. These parameters are those that are measured and which go into the creep controller.

${\displaystyle {\mbox{creep}}={\frac {({\mbox{wheel speed}}-{\mbox{locomotive speed}})}{({\mbox{locomotive speed}})}}\,}$

Sanding

On an adhesion railway, most locomotives will have a sand containment vessel. Properly dried sand can be dropped onto the rail to improve traction under slippery conditions. The sand is most often applied using compressed air via tower, crane, silo or train. When an engine slips, particularly when starting a heavy train, sand applied at the front of the driving wheels greatly aids in tractive effort causing the train to "lift", or to commence the motion intended by the engine driver.

Sanding however also has some negative effects. It can cause a "sandfilm", which consists of crushed sand, that is compressed to a film on the track where the wheels make contact. Together with some moisture on the track, which acts as a light adhesive and keeps the applied sand on the track, the wheels "bake" the crushed sand into a more solid layer of sand. Because the sand is applied to the first wheels on the locomotive, the following wheels may run, at least partially and for a limited time, on a layer of sand (sandfilm). While traveling this means that electric locomotives may lose contact with the track-ground, causing the locomotive to create electromagnetic interference and currents through the couplers. In standstill, when the locomotive is parked, track circuits may detect an empty track because the locomotive is electrically isolated from the track.

See also

• Booster engine
• Curve resistance
• Friction
• Frictional contact mechanics
• Hunting oscillation
• List of steepest gradients on adhesion railways
• Rail squeal
• Railway tire
• Rolling resistance
• Sandbox (locomotive)
• Slippery rail
• Traction
• Tribology
• Wheelset
• Wheelskate

Footnotes

1. "Combined Adhesion ad Cog-Wheel Railways". The Railway News and Joint Stock Journal. 51 (1307). London: 100–101. January 19, 1889.
2. Engineering Mechanics. PHI Learning Pvt. Ltd. 2013-01-01. ISBN 9788120342941.
3. Shoukat Choudhury, M.A.A; Thornhill, N. F.; Shah, S.L (2005). "Modelling valve stiction". Control Engineering Practice. 13 (5): 641–58. CiteSeerX 10.1.1.135.3387. doi:10.1016/j.conengprac.2004.05.005.
4. École Polytechnique Fédérale de Lausanne. "Traction Electrique - Principes de base" (PDF).
5. "EPR 012: Testing of locomotive all weather adhesion" (PDF). RailCorp. October 2011. Archived from the original (PDF) on June 21, 2014. Retrieved October 25, 2014.
6. "Book : The Contact Patch".
7. ^ Okamoto, Isao (March 1999). "Shinkansen Bogies" (PDF). Japan Railway & Transport Review. Vol. 19. ISSN 1342-7512. Archived from the original (PDF) on 2014-11-06. Retrieved 2017-11-30.
8. "Science of Railway Locomotion". www.brooklynrail.net. Archived from the original on 2016-03-06. Retrieved 2016-02-04.
9. Wickens (2003), p. 6, Section 1.3 Creep (see Fig. 1.5a)
10. See *Деев В.В., Ильин Г.А., Афонин Г.С. (in Russian) "Тяга поездов" (Traction of trains) Учебное пособие. - М.: Транспорт, 1987. - Fig. 2.3 p.30 for a curve (which is linear at first) relating creep to tangential force
11. Heavy Freight Locomotives Of Britain, Denis Griffiths 1993, Patrick Stephens Ltd, ISBN 1-85260-399-2 p.165
12. "The Red Devil and Other Tales From The Steam Age" by D.Wardale, (1998) ISBN 0-9529998-0-3, p.496
13. http://ewp.rpi.edu/hartford/~ernesto/S2015/FWLM/OtherSuppMtls/AdditionalPapers/Olofsson-Tribology-Wheel-RailContact.pdf Archived 2017-03-29 at the Wayback Machine fig 5.12
14. "Adhesion" (PDF). indianrailways.gov.in. Retrieved 11 April 2023.
15. "Locomotive Sanding Systems & Rail Traction | Cyclonaire". Cyclonaire. Archived from the original on 2015-10-18. Retrieved 2016-02-04.
16. "The Adhesion Rail Riddle - Ensuring Trains Can Brake | Engineering and the Environment | University of Southampton". www.southampton.ac.uk. Retrieved 2016-02-04.
17. Bernd Sengespeick (2013-08-08). "Hybrid vehicle air conditioning service" (PDF). EBA. Archived from the original (PDF) on 2016-09-17. Retrieved 2013-08-08.

Sources

• Carter, F. W. (July 25, 1928). On the Stability of Running of Locomotives. Proc. Royal Society.
• Inglis, Sir Charles (1951). Applied Mathematics for Engineers. Cambridge University Press. pp. 194–195.
• Wickens, A. H. (1965–1966). "The Dynamics of Railway Vehicles on Straight Track: Fundamental Considerations of Lateral Stability". Proc. Inst. Mech. Eng.: 29.
• Wickens, A. H.; Gilchrist, A O; Hobbs, A E W (1969–1970). Suspension Design for High-Performance Two-Axle Freight Vehicles. Proc. Inst. Mech. Eng. p. 22. by A H Wickens
• Wickens, A. H. (Jan 1, 2003). Fundamentals of rail vehicle dynamics : guidance and stability. Swets & Zeitlinger.

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