Research Article | Open Access

Volume 2013 |Article ID 703202 | https://doi.org/10.5402/2013/703202

Matthias Scherge, Roman Böttcher, Mike Richter, Udo Gurgel, "High-Speed Ice Friction Experiments under Lab Conditions: On the Influence of Speed and Normal Force", International Scholarly Research Notices, vol. 2013, Article ID 703202, 6 pages, 2013. https://doi.org/10.5402/2013/703202

# High-Speed Ice Friction Experiments under Lab Conditions: On the Influence of Speed and Normal Force

Accepted23 Oct 2012
Published02 Dec 2012

#### 1. Introduction

The precise knowledge of the coefficient of friction is of crucial interest for people designing bobsled tracks, organizers, and technicians. The faster the sleds can travel on the run, the more thrilling the race. But the track must not be too fast: the crew still needs to be able to reach the bottom safely. So engineers have to calculate and simulate exactly how fast a sled can travel on specific sections of the track. The calculations are mainly based on the coefficient of friction between the runners and the ice. The second great impact on speed is aerodynamic drag, which was not investigated here.

Generally, the number of experiments in the past dealing with friction measurements for the system steel versus ice is limited [1, 2]. Most of the data were obtained with tribometers (e.g., [3, 4]) or special devices (e.g., [1, 5]). In the following section, results closest to the system runner/ice will be reviewed. We concentrate on a temperature range between −2°C and −12°C.

Evans et al. determined low-friction coefficients by sliding steel on an ice cylinder at a sliding speed = 1–15 m/s at −11.5°C. ranged from 0.01 to 0.03 . Similar friction coefficients of about 0.02 were obtained in reciprocating tribometer tests at quasi-static conditions ( = 1.5 × 10−7 m/s to 7.4 × 10−3 m/s) at rather high pressure of 270 MPa and an ice temperature of −10°C . A 60 kg sled was constructed by Itagaki et al. and was moved across ice at a speed of 1.5 m/s. The length of the runners was about 30 cm, thus it can be assumed that the acting pressure was less than 10 MPa. For a smooth runner at = −5°C, a coefficient of friction of 0.01 was obtained . Based on ice tribometer experiments at = 1 m/s and = −2°C, Hainzlmaier published coefficients of friction on the order of 0.05 showing a moderate decrease as function of pressure (0.5–6.5 MPa) . Dumm carried out tribometer tests at 2 m/s and an ice temperature of −2°C using rectangular steel sliders (4 mm × 8 mm) and obtained coefficients of friction between 0.01 and 0.02. The pressure range was 1 to 8 MPa . Mills performed experiments with a tribometer as well and measured coefficients of friction between 0.04 and 0.06 for a pressure range between 0.1 MPa and 1 MPa at = 2 cm/s and = −2°C . Friction decreased to 0.02 when the sliding speed was increased to 3.4 m/s. In an experiment with a steel ring pressed against the ice, torsion was measured to determine the coefficient of friction. With a pressure of 0.2 MPa, = 0–3 m/s and = −10°C similar results ( = 0.02–0.04) were obtained like Tusima .

Data on ultra-low friction coefficients were published by Niven who measured friction between slider and ring ice at 0.9 m/s and found = 0.002 at = −2°C .

De Koning et al. analyzed ice skates . The mean coefficients of friction for straights and curves were 0.0046 and 0.0059, respectively. Similar results were obtained by Federolf and coworkers . The friction between an ice hockey blade and ice ( = −5.7°C and −4.9°C, = 1.8 m/s) was in the range of 0.0071. The acting pressure was not given. Recently, Poirier published friction data for the bobsled obtained on the base of precise speed measurement by radar . Averaging high- and low-speed data, a mean coefficient of friction of 0.0053 was obtained. More data can be found in a review by Itagaki et al. .

It is obvious that the measured values vary over a wide range. Up to now, the main problem has been the difficulty of measuring friction over a larger range of high speeds and realistic loads. Thus, the data collected only reflect a small fraction of boundary conditions and, sometimes, seem to be rather far from reality. We therefore introduce a new device for high-speed friction tests at realistic loads. This measuring device allows us to ascertain the precise level of friction between the sled and the ice for bobsled runners with different cross-sectional radii.

#### 2. Experiments

##### 2.1. Test Cell and Preparation of Ice

All tests were carried out in a tire test stand. The main piece of the stand is a large drum which is 3.8 meters in diameter and open on one side, situated in a cooled cell, see Figure 1. On the inside of the drum is a layer of ice, on which the model runners slide. A hydraulic cylinder presses the runner to the ice, simulating the weight of the sled and the crew. Whenever the drum rotates, the ice moves out from under the runner, slightly displacing both it and the attached friction force sensor. So instead of remaining at the lowest point, the runner is carried along a little by the rotating drum. Just how far depends on the amount of friction between the runner and the ice. The maximum speed of the test rig is 150 km/h. In our study we confined the speed range to 100 km/h to reduce the noise level in order to detect the expected ultra-low coefficients of friction.

The cooling of the test cell and the drum was started two days before the measurements. The air in the cell was constantly circulated, and the temperature was maintained constant at −5°C. One day before the measurement the ice production was started with a flow of distilled water into the rotating drum. The drum turned at 10 km/h and moved the water, until a constant thin film of ice was formed. The ice production was ended at an ice thickness of about 3 cm. On the day of the test, the ice surface was smoothed by a two-stage process. First, the rough spots were removed with a steel blade. Then the final polishing was performed with a smooth low-profile tire. During this process the tire was rotated at constant speed and the drum rotated as well.

By means of a hydrostat the normal force was exerted to the runner. The normal force range between 100 N and 500 N was chosen to simulate a 2-men (man and female) as well as a 4-men bobsleigh. For example, with the selected length of the model runner an applied normal force of about 200 N corresponded to the load of a 4-men bob sleigh. The force range between 200 N and 500 N was selected to simulate curves. Thus, with the used sample geometry of the model runner a pressure range between 20 MPa and 64 MPa was covered.

##### 2.2. Preparation of Runners

The bob runners were made of F.I.B.T. steel 1.4057. Figure 2 shows a drawing of the cross-section and a photograph of the runner after surface finish. For the cross-sectional radius of the runner 4 mm and 8 mm were chosen. To realize a flat contact with the drum, each runner was furnished with a rocker radius of 3.8 m. All runners had a length of 15 cm. Both ends were rounded to prevent the runner from scratching the ice. Thus, the length in flat contact with the ice was 10 cm.

The runners were prepared according to the F.I.B.T. regulations following a procedure used in competition. The runners were first polished with sand paper with decreasing grit size followed by a treatment with diamond slurry. Neither machines nor special grinding fluids were applied.

As a result, the surface of the runner showed low roughness as demonstrated in Figure 3. The average roughness was 9 nm and the peak-to-valley roughness was 118 nm.

##### 2.3. Data Acquisition

All force data were measured using a three-axis sensor (K3D120, ME Messsysteme GmbH, Germany) with a maximum load of 1,000 N. The sensor is very compact with a lateral dimension of 120 mm × 120 mm and a height of 30 mm. The sensor comes with integrated electronics allowing the separate evaluation of forces in lateral ( and ) as well as vertical direction (). The crosstalk from to and at 500 N is less than 1%. Before friction measurements the sensor was calibrated using designated dead weights. The sensor was then connected to a PC using USB. During all tests both normal () and tangential forces () were recorded at a sampling rate of 1,000 Hz. To remove noise, the data were low-pass filtered and averaged. To verify the repeatability of the measurements, selected stressing points, that is, a pair of speed and normal force, were tested several times to obtain the error bars. In the diagrams the error bars were always smaller than the size of the symbol.

In order to initiate the measurements, the drum was set in motion and the speed was set. Then, the sensor assembly was slowly lowered until the -sensor displayed the desired normal force.

#### 3. Results

##### 3.1. Friction as Function of Speed

The speed dependence was recorded between 2.8 m/s and 28 m/s (i.e., 10 km/h and 100 km/h) with increments of 2.8 m/s at a constant load of 500 N, see Figure 4. For both runners a new position on the ice was selected and a linear decrease of the coefficient of friction as function of speed was measured. At a speed of 2.8 m/s friction showed values between 0.015 and 0.016. At highest speed friction ranged between 0.005 and 0.008. The straight line shows an extrapolation to higher speeds as discussed later. Taking the error bars into account, both curves show similar behavior.

##### 3.2. Friction as Function of Load

At a constant speed of 14 m/s (50 km/h) the runners were subjected to 5 different loads from 100 N to 500 N, see Figure 5. For each normal force a new track on the ice was selected. Between 100 N and 300 N the coefficients of friction significantly decreased, but remained approximately constant for higher loads. For loads higher than 200 N the coefficients of friction of the 4 mm runner were considered constant. For the 8 mm runner constant friction appeared at 400 N. At higher loads the coefficients of friction run together and showed a value of about 0.011.

The normal forces indicated by the arrows correspond to the loads of either a 2-men bob (women) of 340 kg or a 4-men bob (630 kg). That means that a normal force in the lab-experiment of about 130 N is used to simulate the 340 kg and the lab force of 205 N corresponds to 630 kg.

##### 3.3. Ice Fracture

Depending on the normal force, wear marks were detected on the ice after the tests. Due to surface irregularities, intermitted wear marks were detected for small normal forces, see Figure 6(b). When the normal force increased, continuous wear marks appeared. The highest load of 500 N caused the widest wear track. In addition, ice debris at the flanks of the runner was detected.

#### 4. Discussion

##### 4.1. The Speed Behavior

In the experiments analyzing friction as function of speed the lowest coefficients of friction showed an average value of 0.007 at highest speed. With increasing speed, data scatter increased due to higher mechanical noise. When the linear fit is extrapolated to a speed of 33 m/s (120 km/h), the coefficient of friction decreases to a value of 0.005. This value corresponds very well with measurements of Poirier .

In Section 1 it was shown that the results of most other groups indicate higher friction coefficients than shown in this paper. Figure 7 shows a summary of literature data combined with results from this work. We use the friction coefficients given in Section 1 and data provided by Itagaki et al. .

Our own data represent the average of the friction coefficients obtained for the 4 mm and the 8 mm cross-sectional radius. The foreign data originate mainly from tests in a pressure range between 1 MPa and 10 MPa and ice temperatures between −2°C and −12°C. One experiment was carried out at 270 MPa. Except the results of Niven,  all coefficients of friction can be approximated by a master curve. With this diagram it can be concluded that—as long as ice fracture is low—the sliding speed is of crucial importance for the magnitude of the coefficient of friction. Moreover, Figure 7 suggests that two distinct friction regimes exist. Up to a speed of about 3 m/s the strongest decrease in friction can be observed. For higher speeds the coefficient of friction decreases with constant but significantly smaller slope. It can be speculated that the ability to generate more free water with increasing power of friction saturates at higher sliding speeds. However, to prove this would go beyond the scope of this paper and is reserved for future work.

The acting load presses the runner onto the ice. Both runner and ice are, to a certain degree, elastic media following Hooke’s law, . The stress is proportional to strain with Youngs modulus as proportionality constant. Exceeding the compressive failure stress the ice breaks or shows the first defects, that is, holes or dimples. In Figure 6, we showed that ice fractured after loading and sliding. Hainzlmaier showed that especially in the curves, grooves with a depth of about 180 μm in the ice were detected . According to literature the compressive failure stress of ice ranges between 1 MPa and about 40 MPa, depending on ice temperature and strain rate [15, 16]. A review of literature data showed a compressive failure stress of about 25 MPa at a strain rate of 103 s−1 . At a strain rate of 104 s−1—achieved with our setup at 28 m/s—ice ( = −10°C) can develop a compressive failure stress of more than 40 MPa . The impact of compressive failure stress on friction can be seen in Figure 5. At a certain normal force, that is, >200 N for the 4 mm runner and >400 N for the 8 mm runner, the coefficients of friction became constant. The question is how the compressive failure stress is related to the friction coefficient. To answer this question, Hertzian contact mechanics  was applied to calculate the acting pressure between runner and ice for elastic boundary conditions, see Figure 8. The inset of the figure shows the reduced mechanical setup. We treat the section of the model runner that is in contact with the ice as cylinder with the length = 10 cm. Supplying the values for acting normal force and cross-sectional radius (4 mm and 8 mm) to (1), the maximum pressure and the contact width were calculated: with and are Youngs moduli of steel (210 GPa) and ice 9.31 GPa, is the cross-sectional radius of the cylinder, and , since the ice was treated as flat surface. is the Poisson ratio of 0.33 . With the given parameters, the contact width ranges between 20 μm and 60 μm.

The compressive failure stress of 40 MPa was attained at 200 N for the 4 mm runner and for the 8 mm runner at 400 N. This corresponds well with the findings shown in Figure 5. For higher normal forces Figure 8 loses its meaning, since ice fractures and structural defects of the ice are the consequences . Due to cracked ice the wear track becomes wider, thus, the real area of contact becomes larger.

Increasing normal force as well as increasing speed decreases the friction force by lowering the shear stress due to generation of a thin water film 

However, with increasing contact area both influences seem to equilibrate and friction becomes constant for normal forces higher than 200 N (4 mm runner) and higher than 400 N (8 mm runner). A detailed analysis of using a microtribometer will be subject of a future study.

While the coefficient of friction at the load point of a 4-men bob is located in the constant section of the friction curve of Figure 5, the friction coefficients in the load range of the 2-men bob significantly changes with load. This means that for the 2-men bob the addition of ballast (if possible) has a strong impact on the coefficient of friction, thus the speed of the bob. For the 4-men bob this influence can be neglected.

#### 5. Conclusions

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