Tire speed ratings derive from regulatory testing in which tire structural integrity is validated over a series of steps with successively increasing speed. For the FMVSS 139 high-speed standard, there are four half-hour duration speed steps at 80, 140, 150, and 160 kph. Speed ratings from Q through Y may be attained through the UN ECE R30 regulation high-speed testing. For either protocol, a tire must demonstrate the ability to operate without crack development at high speed for a specified period. After the test, “there shall be no evidence of tread, sidewall, ply, cord, inner liner, belt or bead separation, chunking, broken cords, cracking, or open splices.” A workflow for simulating regulatory high-speed durability performance has been developed based upon (1) recent improvements to the Abaqus steady-state transport formulation that now permit converged solutions to be obtained at high speed (including after the development of standing waves in the tire) and (2) Endurica DT self-heating and incremental fatigue simulations that account for thermal effects and for damage accumulation occurring due to a schedule of load cases. The self-heating calculation features the Kraus model and accurately captures viscoelastic loss modulus dependence on strain amplitude and temperature. For each step of the high-speed procedure, steady-state structural and thermal solutions are first computed. The deformation history in the presence of standing waves is shown to require rainflow counting due to the occurrence of multiple load cycles per tire revolution. Crack growth is finally integrated for each potential critical plane through each step of the test until failure is indicated. Standing waves at high speed induce significant self-heating and damage, rapidly limiting high-speed performance. The temperature dependence of self-heating and strength properties also plays a major role in limiting high-speed durability. The simulations were executed on both a flat surface and on the regulation specified 1.7 m diameter road wheel. As expected, durability testing on the road wheel is more severe, and the beneficial effect of a nylon overwrap is predicted.
Durability standards in the tire industry often specify a multistep testing format in which the subject tire is operated over a prescheduled series of increasingly severe conditions. In order to legally qualify as a “safe” tire, the standards [1 ,2 ] specify that there “shall be no visual evidence of tread, sidewall, ply, cord, inner liner, or bead separation, chunking, broken cords, cracking, or open splices.” For example, the high-speed tests specified in the FMVSS 139 regulation and in the UN ECE R30 regulation both involve multiple steps of increasing tire speed. The three-step durability test with increasing load, specified in FMVSS 119, is another example. For tires that pass these minimum requirements with no obvious damage, it is also possible for tire makers to augment the regulation testing schedules with additional steps at over-load and/or over-speed conditions. Probing the ultimate limits of the tire's capacity gives engineers evidence to support development program imperatives to maintain or enhance durability performance.
In contrast, tire durability simulations have traditionally been abbreviated to a single operating condition [3 –11 ]. This simplification reduces analysis complexity and cost while still providing a form of relative guidance, but it gets in the way of matching up simulation results with regulatory test results. The aim of this work is to establish and demonstrate durability simulation procedures that address the multistep features of the regulatory testing protocols and provide insights into the effects of the progression of damage during the test.
The procedures are specified in Table 1. This protocol combines the FMVSS 139 high-speed requirement [1 ] and the UN ECE R30 speed rating test [2 ]. The subject tire has size P195/85R17 with a Tire & Rim Association (T&RA) 100% load of 8380 N under 220 kPa of controlled inflation pressure. The tire was modeled at steady-state rolling on both a 1.7 m road wheel and on a flat road surface.
The analysis begins by obtaining finite element solutions for the steady-state rolling tire at each step of Table 1. For each step, both a structural and a thermal solution were computed. Because of high speeds, it was necessary for the structural solution to capture standing waves [12–16 ]. The steady-state solutions were obtained using Abaqus 2019, which features enhanced convergence for rolling structures at high speed. The dissipation field used in computing the thermal solution was generated in Endurica CL using the Kraus model of loss modulus dependence on strain amplitude, with account taken of the temperature dependence of viscoelastic dissipation. Finally, the damage occurring during each test step was accrued using the Endurica DT incremental fatigue solver. The dependence of the crack growth rate law on temperature was considered using the table-lookup functionality provided by Endurica DT.
Steady-State Rolling Structural Analysis
The material parameter C10 is listed in the Table 2, while the parameter D1 is chosen such that Poisson's ratio is 0.495.
The belts and the plies were represented via the Marlow [17 ] stress–strain law, which enabled a tabular specification of the nonlinear elastic stress–strain curve. A linear elastic model was used to represent the bead wire.
A P195/75R17 grooved symmetric tire is used to carry out all the simulations. A cross-sectional view with the finite element mesh, overall dimensions, and a detail construction of the tire is shown in Figs. 1 and 2.
The axisymmetric finite element model uses all rubber compounds described in Table 2 as solid elements including the bead wire. The plies, the belts, and the overwrap are modeled as surface elements, which are then embedded into the solid elements.
In order to simplify the model, a rigid body constraint is applied to represent the tire rim. The highlighted nodes of the tire carcass in Fig. 3 are used to form a rigid body constraint with the rim axle located at the center of the axis of revolution.
A simulation was set up to inflate the tire to 220 kPa pressure in the axisymmetric model. The simulation results from the inflation analysis were transferred to the three-dimensional (3D) tire model using the symmetric model generation and the symmetric results transfer technique available in Abaqus. This technique generates a 3D tire mesh from the axisymmetric model with user defined discretization along the circumference of the tire. A uniform angle of 3° sectors was created around the circumference of the tire as shown in Fig. 4. Although it is common to focus circumferential refinement in the tire footprint for steady-state analyses, in the present work the uniform mesh was specified in order to properly resolve standing waves.
The 3D tire model was set up to simulate the footprint analysis with two different load cases: 8380 N (1884 lbf) and 7123 N (1601 lbf ). These loads were taken from the T&RA handbook representing 100% and 85 % of rated load, respectively. The footprint analysis was conducted initially on a 1.7 m diameter drum as shown in Fig. 4. The drum is modeled as a rigid surface, and the contact between the tire and the drum was modeled with a coulomb friction coefficient of 0.8.
Additional simulations were also performed by replacing the drum with a flat surface to quantify the impact of roadwheel curvature on tire damage.
The 3D loaded tire was used to perform the steady-state rolling analysis under the speeds listed in Table 1.
Steady-State Rolling Theory
Simulation of dynamics of a tire using the steady-state rolling theory is frequently carried out using Abaqus: A Dassault Systemes Simulia brand finite element code [18–22 ]. A general purpose, steady-state transport theorem implemented in Abaqus makes it possible to simulate most of the tire rolling phenomena that exhibit steady-state behavior such as rolling on a drum or on a flat surface. The alternative to the steady-state rolling is to use either a transient implicit or an explicit rolling simulation. However, the cost of the implicit and the explicit rolling, in both the fidelity of the finite element model and the simulation runtime, makes these approaches impractical.
Steady-state transport analysis takes advantage of the fact that a steady-state solution is possible for a tire that is traveling at a constant ground velocity and a constant angular rolling velocity. The steady-state transport analysis uses a reference frame attached to the axle of the tire. This special reference frame removes explicit time dependence from the problem, so that a purely spatially dependent analysis can be performed. The finite element mesh describing the tire in this frame of reference remains stationary. This kinematic description can be viewed as a mixed Eulerian/Lagrangian formulation, where the rigid body rotation is described in an Eulerian manner and the deformation is measured in a Lagrangian manner.
Consider the case shown in Fig. 5(a), where a cylindrical body is rotating with a constant angular rolling velocity ω around a rigid axle T at X0, which in turn rotates with constant angular velocity Ω around the fixed cornering axis n through point Xc [22 ].
The inertial forces are evaluated along the streamlines of the rolling tire by using standard Galerkin methods. However, when the inertial forces become significant, at higher rolling speeds, the solution starts to diverge as the tire becomes unstable at the onset of the standing waves. A recent development in Abaqus steady-state transport analysis addresses this divergence problem by introducing a weighted shape function in the Galerkin methods. This improved shape function allows a nonuniform convection of the inertial forces along the circumference: from the leading edge to the trailing edge of the tire. As a result, convergence during high-speed rolling can be achieved at and beyond the point where standing waves occur in the tire.
Structural Analysis Workflow
The overall workflow for the structural analyses is shown in Fig. 7. This procedure was executed for each step of the testing protocol. All analyses originated from the same inflation job. Two static footprint jobs were then made, one at 85% load and the other at 100% load. The steady-state rolling procedure for each speed was then started from the static footprint job and equilibrated at the free rolling condition, resulting ultimately in a separate converged solution for each step of the protocol.
A first manifestation of the inertial effects of steady-state rolling is growth of the free rolling radius of the tire. The free rolling radius Rf is computed from Eq. (7), V is specified, ωf is determined by the finite element solution as the angular speed that results in zero driving or braking torque. The free rolling radius is plotted on a per step basis in Fig. 8, and as a function of speed in Fig. 9. The free rolling radius on the 1.7 m road wheel is smaller than on a flat surface at constant load, reflecting lower stiffness and larger deflection. The drum and flat results were computed with the nylon overwrap layer specified in Table 2. The no overwrap case was computed for a flat surface by removing the overwrap rebar layer from the model.
A second manifestation of inertial effects is the development of standing waves in the solution at higher speeds. Figure 10 visualizes standing wave development by plotting the out-of-plane displacement U2 at each step of the test. Only the drum case is shown, since the other cases were quite similar. The standing wave first becomes obvious in step 10 at 210 kph. The occurrence of a standing wave multiplies the number of cycles occurring per tire revolution. Where below the standing wave speed there is a single load cycle per revolution associated with material passage through the footprint, once the standing wave develops, the number of sidewall/tread flex cycles per revolution is multiplied, resulting in much greater self-heating and damage to tire materials.
In order to assess damage occurring during the testing protocol, the temperature field must be computed. Although a fully transient thermal workflow is possible, for the present study, a steady-state workflow was applied for simplicity. In this workflow, the steady-state thermal solution was obtained for each test step using the already obtained corresponding steady-state structural rolling solution. The rolling resistance of the tire was also computed by integrating the dissipation field over the volume of the tire.
Temperature was computed on the same two-dimensional (2D) axisymmetric tire cross-section model that was used for mounting and inflation and relying on the usual assumptions [5 ,8 ,23–27 ] that any thermal gradients in the circumferential direction were zero. The 2D model has 1026 elements and 1146 nodes.
The thermal conductivity of all rubber compounds was taken as 0.25 W/(m K) [28 ]. The thermal conductivity of steel was taken as 50 W/(m K).
The value R = 302 mm was used as the characteristic radius. The reference speed v0 was taken as 20 m/s. The reference film coefficient was taken as 83 W/(m2 K). The sink temperature for external flow was taken as 23 °C.
The interior film coefficient was taken to be constant at a value of 10 W/(m2 K) with a sink temperature of 40 °C. The assumption of constant film coefficient is founded in the thought that air at steady state in the internal cavity is entrained with the tire and therefore has a small relative velocity.
Dissipation rates for each finite element were computed using the Kraus model in the Endurica CL code's microkinematic hysteresis framework. The duration of each tire revolution was specified in the Endurica calculation through the HISTPERIOD parameter, as P = 2π/ωf, where ωf has units of radians per second.
Microkinematic Dissipation Framework
The Endurica CL microkinematic framework enables the kinematic analysis of material line segments and material planes embedded in a finitely deforming material. Line segments and material planes often hold special physical significance. For example, under affine deformations like that shown in Fig. 11, we may associate a material line segment with the end-to-end distance of a polymer chain. Or we may associate a material plane with a particular microcrack or a specific interface in multiphase material. At a given point of interest in a structure, the microkinetmatic analysis is iterated across all possible orientations of a line segment or material plane for the purpose of accumulating a total material response across all orientations. In the present case, the material response of interest is the total heat energy generated per unit volume due to an applied deformation history.
The history of length change or of shearing of a single microkinematic element (line or plane) in a single orientation is not by itself a complete indicator of dissipation. But the cumulative effects of all possible microkinematic elements can be considered by integrating over the unit half sphere representing all orientations (see Fig. 12). The dissipation contribution of each oriented line segment or material plane is computed via a dissipation law, here implemented as the Kraus law [29 ]. The dissipation law relates the extensional strain amplitude or the shear strain amplitude of the microkinematic element to its contribution to total dissipation. The amplitudes are extracted via the same rainflow counting algorithm [30 ,31 ] that is used in the fatigue analysis.
The microkinematic approach offers several advantages. Like the prior art dissipation models of Luchini et al. [26 ] or Terziyski and Kennedy [27 ], the present model avoids a full constitutive description of time-dependent stress–strain behavior and so does not require elaborate experimental or computational procedures. It also guarantees coordinate frame independence, so that dissipation calculations carried out in different reference frames give the same answer for any multiaxial loading history. The microkinematic approach shares some key features with the microsphere models [32–34 ], but again, is not a full stress–strain model and therefore avoids many of the associated computational costs and convergence risks.
Kraus Self-Heating Law
The Kraus law is convenient because it does an excellent job of capturing typical dynamic mechanical analyzer (DMA) data from the rubber lab. For the tread cap region of the tire model, published strain sweep and temperature sweep DMA results [35 ] for a carbon black (CB) filled solution styrene–butadiene rubber (SSBR) tread compound were used here (control compound in that publication). In the absence of other data, the dissipative properties of this compound were applied to all materials in the tire for the sake of simplicity.
The εa,c, , E″max,K, E″0, and E″∞ are fitting parameters, and the values for the SSBR tread compound were determined to be 0.0131, 0.638, 2.07, 1.80, and 1.06 MPa from the fit shown in Fig. 13a.
In this expression, the Kraus model fit provides E″ as a function of strain.
This is valid for linear viscoelastic material with a normal sinusoidal stress output for an applied sinusoidal strain input. This is generally true for filled rubber, which exhibits “linear-nonlinear dichotomy” of viscoelastic behavior [38 ,39 ]. The stress amplitude (σa) is determined from the applied strain amplitude and the magnitude of the complex modulus (|E*|), σa = |E*|εa. To determine the scaling factor, C, in Eq. (12), a simple tension simulation was conducted at a strain amplitude of 0.1, and C was selected to match the simulated hysteresis with the experimental value shown by the arrow in Fig. 13c.
Temperature Sensitivity of Self-Heating Law
Thermal Analysis Workflow
The steady-state thermal analysis workflow executed for each of the steady-state structural solutions obtained is shown in Fig. 15. Owing to the nonlinear dependence of the dissipation rate on temperature that is implicit in Eq. (14), the workflow implemented iterations where strain and temperature fields were passed from Abaqus to Endurica, and dissipation fields were passed from Endurica to Abaqus. Iterations continued until the steady-state temperature fields computed in Abaqus were consistent with the temperature-dependence dissipation fields computed in Endurica. Rolling resistance was also computed for each simulation by integrating the dissipation field over the volume of the tire to obtain a total dissipation and solving the relationship = FrrV for the rolling resistance force Frr given tire rolling speed V.
For each steady-state thermal solution, both the total rolling resistance and the temperature distribution were computed. Figure 16 shows the rolling resistance dependence on test step. Figure 17 (left) shows the dependence on speed. Below approximately 200 kph for this tire, the rolling resistance shows little dependence on speed. In fact, up until 160 kph, there appears to be a very slight decrease in rolling resistance, possibly due to growth of the tire diameter under increasing inertial forces. Increasing inflation pressure is commonly known to produce diameter growth and decrease rolling resistance [40 ,41 ]. Perhaps the effect of increased tire speed is in certain ways similar to increasing inflation pressure. Beyond step 9 of the test, however, there is a rapid increase in rolling resistance. This is clearly associated with development of the standing wave. The rolling resistance of the tire on a roadwheel is shown to be somewhat higher than on a flat road surface, as has been reported many times in past. Removing the overwrap has only a slight effect on tire rolling resistance.
Maximum temperature in the tire, shown in Fig. 17 (right), increases at first on a linear trend with regard to speed but gives way to stronger increases at high speed once the standing wave develops. Temperatures on the 1.7 m road wheel drum were significantly higher than temperatures on a flat road surface, as observed previously [42 ]. Only very slight operating temperature differences are predicted for the comparison of tires with and without overwrap, and there seems to be a crossover in ranking as tire speed increases.
The temperature distributions for drum and flat road cases on the tire cross section are plotted in Fig. 18 for 80, 200, and 300 kph. Again, it is apparent that the drum case runs hotter, especially in the tire shoulder and the lower sidewall. Presumably this is associated with the larger deflection attained at constant load on the drum. It is also apparent that increasing tire speed increases tire operating temperature. Temperatures are also plotted vs test step for the critical belt, sidewall, and tread elements in Fig. 19. The locations for these critical elements are shown in Fig. 20.
Once strain and temperature fields were generated for the steady-state rolling tire at each step of the testing protocol, an assessment was then made of durability. The assessment considers the fracture mechanical properties [43 –49 ] of the rubber compounds. The analysis is based on the incremental, critical plane framework available in Endurica DT and the steady-state rolling feature in Endurica CL. Together, these tools account for the potential development of cracks in all elements of the tire, over the scheduled series of load cases. They also enable the calculation of residual life following the conclusion of each step.
In addition to stress–strain and thermal properties discussed previously, durability analysis requires knowledge of the crack growth rate law of each compound. The basic material models, including strain-crystallization effects, have been described in prior work [50 ]. Owing to the strong temperature dependence on speed, it is essential in addition to consider how the crack growth rate law depends on temperature.
Crack growth rate law and temperature dependence.
The material parameters are the fracture mechanical strength Tc, the power law slope F, and the value of the crack growth rate rc, at which the power law intersects a vertical asymptote placed at Tc. We give in Table 3 a summary of the parameter values chosen for each tire compound in this analysis. In all cases, rc = 1 × 10−2 mm/cyc has been used.
Crack precursor size.
The variables θ and φ in Eq. (16) specify the orientation of the critical plane, which for fully relaxing, simple tension experiments will be oriented perpendicular to the loading direction.
Critical Plane Analysis
Critical plane analysis has been described in detail in earlier reports [55–62 ]. Critical Plane Analysis evaluates potential crack growth at every point in the tire, for every possible orientation a crack might take. In the Endurica CL total formulation, critical plane analysis computes, for each possible point and orientation, the number of repeats Nf of a given duty cycle that are required to grow the crack precursor from its original size c0 to the size cf marking the end of life. The calculation is iterated over all possible values of θ and φ, taking care to identify the particular orientation that minimizes the life prediction. In this sense, critical plane analysis produces the most conservative possible interpretation of the damaging effects for a given stress/strain history.
In evaluating Eq. (16) for variable amplitude histories, it is necessary to identify the constituent constant amplitude events that together produce the total crack growth rate. This is accomplished by means of a rainflow counting operation that is performed on the energy release rate history estimated for the plane specified by θ and φ. The rainflow counting and damage summation operation is iterated for all planes, so that the finally selected critical plane truly reflects the most damaging possible experience across all planes and events. For cases of proportional tension/shear loading, the critical plane method tends to predict cracking aligned with the maximum principle stress direction. For other cases, however, other crack orientations appear as most damaging. In cases of compression and shear, for example, crack closure causes the critical plane to occur with an orientation that maximizes shearing of the crack. It has been shown [63 ] that critical plane analysis accurately predicts the “sideways” orientation of cracks appearing under nonrelaxing loads in strain-crystallizing rubbers.
In this formulation, the crack growth rate law r is integrated from the beginning of cycle Ni to its final cycle Ni+1. The result of the integration is the change of length of a crack Δci→i+1,j,k for each plane j and element k of the model. The accumulated crack lengths for each element are written to a file during the analysis, so that future additions of load history may begin at the point at which the prior increment left off. In this scheme, there is no requirement that the duty cycle during one increment be the same as the duty cycle in subsequent increments. The crack length may be updated in as many increments as are needed to represent the testing schedule. The combination of the critical plane analysis with the incremental solution method is quite powerful, enabling accurate damage accounting of arbitrary compositions of multiaxial, variable amplitude loading history.
From the user perspective, the incremental workflow is implemented as a series of successive Endurica DT analyses, each with its own load case and RESTART output request specifying the number of repeats to be applied for the step.
Residual Life Calculations
A special case of the incremental analysis yields the residual life calculation. In order to quantify remaining life at any given step, a nominal metric duty cycle may be defined (in the present study, 85% load at 80 kph has been used), and the number of repeats of this nominal cycle is computed for the hypothetical case where the nominal cycle is repeated ad infinitum until end of life (when the crack reaches length cf), starting with the damage state/crack length existing at the end of step i.
Endurica DT returns the residual life when the initial damage state of the model is set to the state recorded in the restart file from the end of the history. To compute residual life, the integration is continued from the end of the history until end of life is reached.
Durability Analysis Workflow
Figure 22 illustrates the workflow that was used for analysis of the high-speed durability testing protocol. Each step of the protocol was first divided into two substeps in order to approximately address the thermal transience of each step. The first substep in all cases had a duration of 5 minutes and was computed using the temperature field from the prior step. The second substep covered the remainder of the total step duration using the steady-state temperature field from the current step. Within each step, three durability calculations were made. First, the total life for the current step was computed with Endurica CL. This calculation gives the total number of tire revolutions required to reach end of life in the case that the tire operates at constant load and speed equal to the current step. Second, the damage state (i.e., crack length in each element) at the end of each step was computed using Endurica DT's implementation of Eq. (17) to integrate from the crack size at the end of the prior step to the crack size at the end of the current step. These results are written to a restart file that is later used to start integration of the subsequent step. Third, the residual life remaining following the end of the present step was computed with Endurica DT, again using Eq. (17) but now allowing the upper limit of integration to run out to end of life. For this calculation, the first step of the protocol is used as a reference load case. In other words, we compute tire revolutions under step 1 loading that would be required to grow the crack from the end of the step to end of life.
The fatigue analysis identified critical regions of the tire in the belt gum, in the sidewall, and in the tread material. The critical elements are shown on the tire cross section in Fig. 20. Each element is displayed with its local element coordinate system. The local element coordinate systems were generated by copying the global system, so that the 1 (x) direction points toward the right, and the 2 (y) direction points upward.
For each of the critical elements, the distribution of fatigue life over all orientations is visualized via the damage sphere, as shown in frames b, c, and d of Figs. 23–25. On the damage sphere, red represents orientations with shortest life, and blue represents orientations with longest life. Outward pointing vectors are drawn on each sphere to represent the normal to the most favorable cracking planes. Note that the sphere orientation in these figures matches the coordinate system shown in frame a. The history of cracking energy density on the most critical plane is also plotted for each case in frames e, f, and g. Generally, all of the histories show that at low speed, a single load–unload cycle occurs as material passes through the tire footprint (centered at 180 degrees). With increased speed, the magnitude of the cracking energy density increases, and the development of standing waves produces multiple load–unload events per tire revolution. In order to properly account for damaging effects of such histories, a rainflow counting algorithm is necessary to identify the individual event pairs to be used in computing the maximum and minimum of each cycle and the crack growth rate of each cycle. Most of the histories are seen to be fully relaxing, with the notable exception of the belt edge at high speed. At high speed, the standing wave imposes many nonrelaxing cycles of significant amplitude on the belt edge. This result suggests that the strain-crystallization properties of the belt gum compound, which are apparent under nonrelaxing cycles, may be especially relevant at high speed.
The belt edge and tread element results show that there are two simultaneous critical planes situated at roughly 90 degrees from each other. This result is typical of a fully reversed simple shearing deformation cycle, consistent with the expected deformations associated with flattening of a curved composite beam (i.e., the belt package). The belt element shearing seems most pronounced in the 1–3 plane, and the tread element shearing in the 1–2 plane. The sidewall element results show a single critical plane that is oriented along the tension direction.
Prior to executing the Endurica DT incremental workflow to accumulate damage across all load cases, it is useful to execute the Endurica CL total workflow to understand the fatigue life of each individual load case on its own. The results of these total fatigue life calculations, for each step applied on its own, is shown in Fig. 26. The results shown are for the belt edge element, which was the most critical. The onset of the standing wave is seen to strongly reduce the life that would be expected at each step, to the point that the life is reduced to 100 cycles by step 11 for the drum road wheel case, and by step 13 for the flat road surface case. The strong reduction in life owes both to the strong decrease of tearing energy with temperature and to the multiplication of deformation cycles per tire revolution and its associated impact on tire operating temperature. The results are plotted vs speed in Fig. 27. If one were to apply Miner's rule using these results, the damage rate per cycle would be equal to one per life from these results. Therefore, the inverse of life can be viewed approximately as a measure of damage rate per cycle. The significant decrease of life at step H corresponds to development of the standing wave and indicates an increase of damage rate in going from U to H of an order of magnitude and in going from H to V of 4 orders of magnitude!
The final incremental analysis with Endurica DT is shown in Figs. 28 and 29. The incremental analysis takes account of the test step durations applied. For purposes of analysis, and in order to approximately represent the thermal transient at each step, each step was broken into two increments. The first increment had a duration of 5 minutes and was simulated using the steady-state temperature field of the prior step. The second and final increment of each step was run for the remaining duration of each step and was simulated using the steady-state temperature field of the step. The life that is reported here is the residual life, computed in terms of repeats of the first load case of the series that would be endured following the steps applied up to that point in the history. Because the initial load steps are so light relative to the capacity of the tire, and because the steps have such short durations relative to the potential life under those conditions, it can be seen that initial steps in the testing do very little to reduce the residual life of the tire.
Expanding the ordinate scale in Fig. 29 shows the progressive degradation occurring throughout the test. Comparing these results with those of the structural and thermal analyses suggests that the acceleration of residual life reduction commences with the development of the standing wave. The effects of the standing wave are quite severe, owing to the multiplication of load–unload cycles per tire revolution, to the strong increase in self-heating and operating temperature, and to the strong decrease of compound strength (and increase of crack growth rate) with increasing temperature. The combination of these factors leads to a precipitous drop of residual life following development of the standing wave. On the road wheel test, this tire is predicted to achieve a speed rating of H. The impact of running the protocol on a flat road surface in lieu of the 1.7 m road wheel is predicted to be an increase from H to V, suggesting that the drum testing does provide a margin of safety relative to the labeling of the tire. For the overwrap vs no overwrap comparison simulated, it is predicted that the tire with overwrap will exhibit marginally better endurance than the tire without overwrap. The margin, however, in the particular case simulated, amounts to less than what would be needed to attain a higher speed rating, just a few minutes or a few tens of kilometers.
The incremental, critical plane fatigue analysis procedures of Endurica DT, combined with the improved convergence at high speed of Abaqus 2019, now make possible the analysis of multistep, high-speed durability schedules with greater detail and accuracy than previously possible.
Tire materials exhibit many “special effects” that must be captured in order to make a proper accounting of damage accrual. The strain amplitude dependence of the viscoelastic loss modulus was specified via the Kraus model with quite high accuracy. For high-speed tests, thermal effects triggered in association with standing waves were shown to dominate, and the temperature dependencies of the viscoelastic and fracture strength laws exhibited a particularly strong influence on the speed rating achieved in the simulation. The table-lookup functions of the Endurica DT incremental solver are especially convenient for accurately capturing such effects.
The effects of standing waves on predictions of rolling resistance and operating temperature are consistent with previously reported behavior. In particular, the weak dependence of rolling resistance on speed below the standing wave speed was predicted, and the strong increase of dissipation associated with development of standing waves was successfully predicted. Also, the higher rolling resistance of curved vs flat was successfully predicted.
Incremental critical plane analysis of the regulatory high-speed tests provides, for the first time, estimates of the relative damage contribution of each test step and of the residual life following each step. The results suggest that rather little damage is done to the tire in a high-speed test until the very last test steps finally produce strong thermal-induced weakening of the tire materials combined with strongly increasing temperatures.
While the present workflow has incorporated instantaneous temperature dependence in the structural, thermal, and fatigue analysis, it did not fully account for thermal transients and it did not account for any thermochemical changes in material properties due to ageing effects. The incremental framework is fully capable of representing these details, however, and future development of the workflow can be aimed at incorporating these effects as well.
Endurica LLC, 1219 West Main Cross, Suite 201, Findlay, Ohio 45840, USA. Email: firstname.lastname@example.org
Dassault Systemes, 6105 Parkland Boulevard, Mayfield Heights, Ohio 44124, USA