1 State of knowledge
2 Aim of this work
3 Test rig set up
Nomenclature | Value/Type |
---|---|
Kin. viscosity at 40 °C | 92 to 99 mm2/s |
Kin. viscosity at 100 °C | 10.4 to 10.9 mm2/s |
Viscosity index VI | 95 |
Density at 15 °C | 0.879 to 0.886 kg/dm3 |
Additive | 4% Anglamol 99 |
4 Test gears
Pinion | Gear | ||
---|---|---|---|
Normal module | (mm) | 3 | |
Normal pressure angle | (°) | 20 | |
Helix angle | (°) | 0 | |
Face width | (mm) | 22 | 20 |
Number of teeth | (–) | 24 | 36 |
Tip diameter | (mm) | 78.32 | 114.7 |
Usable tip diameter | (mm) | 78.32 | 113.9 |
Tip edge radius | (mm) | – | 0.75 |
Tip relief amount | (µm) | ≈ 400 | – |
Modification length | (mm) | 2 | – |
Transverse contact ratio | (–) | 1.20 | |
Material | (–) | Steel | Plastic |
Material | Vestakeep 5000G | Vestakeep 4000CF30 |
---|---|---|
Young’s modulus at 23 °C in N/mm2 | 3515 | 23,000 |
Poisson’s ratio | 0.41 | 0.44 |
Density in g/cm3 | 1.30 | 1.40 |
Fiber reinforcement | None | 30% carbon fiber |
5 Experimental investigation of tooth temperature
6 Experimental investigation of flank load carrying capacity
7 Conclusion
8 Nomenclature
Symbol | Entity | Description | Source |
---|---|---|---|
\(a\) | \(mm\) | Center distance | – |
\(A_{G}\) | \(m^{2}\) | Heat dissipating surface of the mechanism housing | [2] |
\(b\) | \(mm\) | Face width | [2] |
\(b_{w}\) | \(mm\) | Common face width of the gear pair | [2] |
\(d_{1}\) | \(mm\) | Pinion diameter | [2] |
\(ED\) | – | Relative tooth-engagement time | [2] |
\(F_{t}\) | \(N\) | Tangential force | [2] |
\(h_{\min }\) | \(\mathrm{\mu}m\) | Minimum lubricant film thickness | – |
\(H_{V}\) | – | Tooth loss factor | [2] |
\(K_{H}\) | – | Factor for tooth flank loading | [2] |
\(k_{w}\) | \(mm^{3}/Nm\) | Factor for tooth flank loading | [2] |
\(k_{\vartheta ,\text{flank}}\) | \(K\cdot \left(m/s\right)^{0.75}\cdot mm^{1.75}/W\) | Flank heat transfer coefficient | [2] |
\(k_{\vartheta ,\mathrm{root}}\) | \(K\cdot \left(m/s\right)^{0.75}\cdot mm^{1.75}/W\) | Root heat transfer coefficient | [2] |
\(\uplambda\) | – | Specific lubricant film thickness | – |
\(n_{2}\) | \(\min ^{-1}\) | Speed of (plastic) wheel | – |
\(N_{L}\) | – | Number of load cycles | – |
\(m_{n}\) | \(mm\) | Normal module | [2] |
\(P\) | \(W\) | Power | [2] |
\(R_{\lambda ,G}\) | \(K\cdot m^{2}/W\) | Heat transfer resistance of the gear housing | [2] |
\(S_{\mathrm{Hmin}}\) | – | Required minimum safety factor | [2] |
\(T_{2}\) | \(Nm\) | Torque at (plastic) wheel | – |
\(u\) | – | Gear ratio | [2] |
\(v_{t}\) | \(m/s\) | Circumferential speed | [2] |
\(z\) | – | Number of teeth | [2] |
\(Z_{E}\) | \(\sqrt{N/mm^{2}}\) | Elasticity factor | [2] |
\(Z_{H}\) | – | Zone factor | [2] |
\(Z_{R}\) | – | Surface roughness factor | [2] |
\(Z_{\beta }\) | – | Spiral angle factor | [2] |
\(Z_{\varepsilon }\) | – | Contact ratio factor | [2] |
\(\vartheta _{0}\) | \(^{\circ}C\) | Ambient temperature | [2] |
\(\vartheta _{{d_{w}}}\) | \(K\) | Temp. rise at the pitch point | – |
\(\vartheta _{{d_{Na}}}\) | \(K\) | Temp. rise at utilized tip diameter | – |
\(\vartheta _{{d_{Nf}}}\) | \(K\) | Temp. rise at utilized dedendum diameter | – |
\(\vartheta _{\text{flank}}\) | \(^{\circ}C\) | Flank temperature | [2] |
\(\vartheta _{\mathrm{oil}}\) | \(^{\circ}C\) | Oil temperature | – |
\(\vartheta _{\mathrm{root}}\) | \(^{\circ}C\) | Tooth root temperature | [2] |
\(\mathrm{\mu}\) | – | Coefficient of friction | [2] |
\(\sigma _{H}\) | \(N/mm^{2}\) | Flank pressure at the pitch cylinder | [2] |
\(\sigma _{\text{HlimN}}\) | \(N/mm^{2}\) | Rolling contact fatigue strength | [2] |
\(\sigma _{HP}\) | \(N/mm^{2}\) | Permissible flank pressure | [2] |