Involute Spline Software Free Download

[Esperanza Santrizos]

<div>So I'm trying to model some external involute splines. The one I'm particularly on right now is a 21 tooth JIS D-2001. I won't get much page for my buck spending hours modeling this so I'm wandering if anyone knows of ways or sites that I could draw this quickly. After I get one I'll just pattern it but I'm having a hard time find how to actually draw these. Anyone have suggestions? Thanks for your info.</div><div></div><div></div><div>Most of the answers start with "Go to Design Tab..", but as I understand this tab only appears in assembly mode, so I cannot really use it, since I have no idea where this splined shaft is going to be used.</div><div></div><div></div><div></div><div></div><div></div><div>involute spline software free download</div><div></div><div>Download: https://t.co/6Jwcza9NjG </div><div></div><div></div><div>The Gear Generator does not create true involute profiles by default - there are special (hidden?) steps to export as spline curves. Otherwise the output will be circular arc approximations (might be close enough for your need).</div><div></div><div></div><div>You might be able to find the formula for an involute curve to use in the 2D Sketch Equation Curve, but in the attached I started a method of geometrically laying out an involute spline. You should be able to figure it out from my start (the 5point plot is up to the user to choose angle of resolution). This can also be done geometrically by using a Trace function in Dynamic Simulation, but while this solution is easy once set up - it does require knowledge of Dynamic Simulation environment.</div><div></div><div></div><div>Splines are driven shafts that work by interlocking the grooves of one piece with the teeth of a mating bushing. They are used to facilitate the transmission of rotary motion between two shafts and maintain the alignment of two mated components. Depending on the design requirements and configuration of the system, industry professionals employ a variety of different splines, such as involute splines.</div><div></div><div></div><div>Involute splines feature short and equally spaced teeth that allow for greater strength with more centered stress distribution. They are one of the most commonly used types of spline shaft due to their tendency to self-center, enhanced structural strength, and ease with which they can be adjusted to a variety of dimensions. Types available include:</div><div></div><div></div><div>When designing and selecting an involute spline for an application, there are several factors that designers and engineers should keep in mind to ensure optimal performance. These factors include:</div><div></div><div></div><div>At Grob, Inc., our standard splines are cold formed from 1117 mild steel, but, depending on the needs of the customer, other materials are available. By employing our proprietary Grob Rolling Process, we enhance both the torsional strength and surface finish of our products.</div><div></div><div></div><div>Involute spline couplings are often used in cars, robots, and other machines to connect two shafts and transmit a great torque. Though the spline couplings are used in machine design very early, strength calculation problem of this kind of couplings has not been solved so far. Designers must use an approximation method to conduct strength calculations of the spline couplings at the present situation.</div><div></div><div></div><div></div><div></div><div></div><div></div><div>This paper presents a new FEM to conduct loaded tooth contact analysis and stress calculations of the involute spline couplings. This new FEM has many advantages that commercial software cannot have. For examples, this new FEM can save a lot of computer memories in the contact analysis. So, it can solve all-tooth-contact problem of the spline couplings very precisely and quickly even if number of teeth of the spline becomes very great. But the commercial software cannot solve this problem because of computer memory limit. Also, tooth profile deviations and pitch errors of the spline teeth can be considered very easily and precisely in the contact analysis when the new FEM is used. But it shall be very difficult to do the same analyses if the commercial software is used. Special software is also developed according to the principle of the new FEM.</div><div></div><div></div><div>According to the principle of Linear Programming Method, an optimization model can be built as follows using the two equality Eqs. (17) and (18) through introducing an artificial variable \(Z\). This is the mathematical model that is used to conduct contact analysis of the involute spline couplings in this paper.</div><div></div><div></div><div>3D, FEM are used to calculate the deformation influence coefficients \(a_kj\) and \(a_k ^\primej ^\prime\) along the directions of the common normal of the pairs of contact points of themselves. Also stresses of the spline couplings are analyzed by the 3D, FEM. FEM boundary conditions used to calculate deformation influence coefficients and stresses are given in Fig. 3. For a pair of ideal spline couplings, since all the pairs of the contact teeth have the same contact and stress states, it is necessary only to consider one pair of teeth in the contact and stress analyses. So, this paper uses three-teeth models as shown in Fig. 3 for the contact and stress analyses in order to be able to calculate the deformation influence coefficients precisely. But the contact and stress analyses are only conducted for the middle pair of teeth. In Fig. 3, the hatched boundaries are fixed as FEM boundary conditions.</div><div></div><div></div><div>The shaft and hub splines are fixed along axial directions under three cases (Cases 1, 2 and 3) as shown in Fig. 4. Case 1 is the one that both the external and internal teeth have the same face widths and axial boundaries of the shaft and hub splines are fixed as shown in Fig. 4a. Case 2 is the one that the external and internal teeth have different face widths and the axial boundaries are fixed as shown in Fig. 4b. Case 3 is the one that the external and internal teeth have different face widths and the axial boundaries are fixed as shown in Fig. 4c. In Fig. 4c, one end face is added in the fixed boundaries by comparing Fig. 4c with Fig. 4b in order to investigate the effect of the end face on tooth contact and stress distribution states.</div><div></div><div></div><div>Software used to generate tooth profiles of the splines is developed specially by the author. When the gearing parameters as shown in Table 1 are inputted into the software, tooth profiles of both the external and internal teeth can be generated automatically. Figure 6 is the result of tooth profiles of the splines generated by the developed software. The generated tooth profiles are used to build FEM models of the couplings automatically by other software developed by author.</div><div></div><div></div><div>Figure 7a is a FEM model of assembled spline couplings with the same face widths as shown in Fig. 1b. Figure 7b is the FEM model of the shaft spline only. Since the contact and stress analyses are only conducted for the middle pair of teeth, FEM meshes of the middle pair of teeth are divided to be very fine. As shown in Fig. 7, meshes near to the contact surfaces of the middle pair of teeth and meshes at the tooth roots of the middle pair of teeth are divided to be very fine to obtain reliable calculation results. Contact and stress analyses are conducted for the couplings under the boundary condition of Case 1 as shown in Fig. 4a.</div><div></div><div></div><div>Figure 11 is tooth bending stress distribution at the root along the lead. The abscissa is the tooth longitudinal dimension and the ordinate is the bending stress at the tensile side of tooth root. It is found that the tensile stress is almost a uniform distribution along the lead and the maximum tensile stress is about 121 MPa. This value is about 1/3 of the allowable stress of a pair of gears. So, it can be said that it is also rare for the spline couplings to have bending fatigue failure at the root.</div><div></div><div></div><div>Calculation results are compared between the developed FEM software and the approximation method in Table 2. In Table 2, it is found that tooth contact stress obtained by the FEM software is about 3.4 times greater than the one obtained by the approximation method. The shear stress obtained by the FEM software is about 1.3 times greater than the one obtained by the approximation method. The bending stress obtained by the FEM software is about 1.9 times greater than the one obtained by the approximation method. So, it can be said that the approximation method is not precise enough for strength calculations of the involute spline couplings in machine design.</div><div></div><div></div><div>Contact and stress analyses are also conducted for the spline couplings with difference face widths. Figure 16a is a FEM model of assembled spline couplings with different face widths as shown in Fig. 1c. Figure 16b is the FEM model of the shaft spline only. From Fig. 16, it can be found that the face width of the shaft spline is much wider than that of the hub spline. FEM meshes are divided to be very fine for the middle pair of teeth.</div><div></div><div></div><div>Contact and stress analyses are conducted for the couplings under the boundary condition of Case 3 as shown in Fig. 4c to investigate the effect of different boundary conditions on stress distributions. Calculation results are given in Figs. 23, 24, 25, 26, 27 and 28. By comparing these results with Figs. 17, 18, 19, 20, 21 and 22, it is found that there is very little difference between the boundary conditions Case 2 and Case 3. This means that both the two boundary conditions as shown in Fig. 4b,c can be used for contact and stress analyses of the spline couplings.</div><div></div><div></div><div>Figure 33 is the shear stress distribution on the circumferential surface as shown in Fig. 12 when the tooth profile deviations are considered. It is found that the shear stress distribution has also a great change because of the profile deviations by comparing Fig. 33 with Fig. 13. The maximum shear stress is changed from 33.5 into 69 MPa. This value exceeds the allowable shear stress (for an example, 40 MPa for S45C, a Japanese material). So, the shear fatigue failure at the tooth root shall be the most dangerous failure pattern for the involute spline couplings.</div><div></div><div></div><div>Effects of pitch errors of the spline teeth on tooth contact pressure distributions are investigated here. To be able to realize this investigation, a loaded tooth contact analysis must be conducted for all the pairs of contact teeth of the spline couplings. So, Eq. (10) is extended into Eqs. (28) and (16) is extended into Eq. (29). In Eqs. (28) and (29), \(z\) is the number of teeth of the spline couplings. \(z\) is equal to 14 according to Table 1. Also, \(\alpha _z\) is the total angular deformation of the shaft spline relative to the hub spline. \(T_Z\) is the total external torque of the couplings. \(T_Z\) is 411.6 Nm according to Table 1.</div><div></div><div> df19127ead</div>