ASYMMETRIC SPOKE DESIGN FOR TORSIONAL VIBRATION DAMPERS

Abstract

Torsional vibration dampers (TVDs) having a plurality of spokes that are asymmetric by having a changing spoke thickness in the angular direction with the greatest thickness at the position where the belt torque and the dynamic torque of the TVD act in unison are disclosed. The spokes, which connect a central member to a peripheral rim, include an asymmetrical thickness in an angular direction, as evidenced by a cross-section view transverse to a radial length of each of the plurality of spokes. Engine systems having one of the disclosed TVDs mounted to a shaft are also disclosed, for example a TVD mounted to a crankshaft.

Claims

1. A torsional vibration damper comprising: a hub having a plurality of spokes extending from an outer radial surface of a central member to an inner radial surface of a peripheral rim, each of the plurality of spokes comprising: an asymmetrical thickness in an angular direction, as evidenced by a cross-section view transverse to a radial length of each of the plurality of spokes.

2. The torsional vibration damper of claim 1, wherein, for each of the plurality of spokes, the asymmetrical thickness is greatest where the loading effect of the belt torque and dynamic torque are in unison.

3. The torsional vibration damper of claim 1, wherein, for each of the plurality of spokes, the asymmetrical thickness increases from a leading face to a trailing face.

4. The torsional vibration damper of claim 1, wherein, for each of the plurality of spokes, the asymmetrical thickness increases from the leading face to the trailing face as a linear function, as a hyperbolic function, or as a parabolic function mirrored on opposing radial faces.

5. The torsional vibration damper of claim 1, wherein, for each of the plurality of spokes, the asymmetrical thickness increases from the leading face to the trailing face as a first linear function changing to a second linear function that is different than the first linear function mirrored on opposing radial faces.

6. The torsional vibration damper of claim 1, wherein, for each of the plurality of spokes, the asymmetrical thickness increases from the leading face to the trailing face as a nonlinear function changing to a linear function mirrored on opposing radial faces or as a linear function changing to a nonlinear function on opposing radial faces.

7. The torsional vibration damper of claim 1, further comprising an inertia member concentric about the hub with an elastomeric member operatively positioned therebetween.

8. The torsional vibration damper of claim 1, wherein the hub comprises gray cast iron.

9. An engine system comprising: a torsional vibration damper of claim 1 mounted to a shaft for rotation therewith.

10. A front end accessory drive system comprising: a torsional vibration damper of claim 1 mounted to a crankshaft for rotation therewith.

Description

BRIEF DESCRIPTION OF DRAWINGS

[0008] Many aspects of the disclosure can be better understood with reference to the following drawings. The components in the drawings are not necessarily to scale, emphasis instead being placed upon clearly illustrating the principles of the present disclosure. Moreover, in the drawings, like reference numerals designate corresponding parts throughout the several views.

[0009] The patent or application file contains at least one figure executed in color. Copies of this patent or patent application publication with color figure(s) will be provided by the Office upon request and payment of the necessary fee.

[0010] FIG. 1 is a perspective view of components in a front end accessory drive system.

[0011] FIG. 2 is a perspective, longitudinal cross-sectional view of a prior art torsional vibration damper.

[0012] FIG. 3 is a 3D plot of a finite element model of a prior art hub having conventional spokes.

[0013] FIG. 4 is a 3D plot of a finite element model of a hub having asymmetric spokes as disclosed herein.

[0014] FIG. 5 is a perspective, sectional view through one asymmetrical spoke of a hub as a transverse cross-sectional view through the spoke relative to its radial length.

[0015] FIGS. 6A-6E are plan views of alternate transverse cross-sections through a spoke per the view in FIG. 5.

DESCRIPTION

[0016] Reference is now made in detail to the description of the embodiments as illustrated in the drawings. While several embodiments are described in connection with these drawings, there is no intent to limit the disclosure to the embodiment or embodiments disclosed herein. On the contrary, the intent is to cover all alternatives, modifications, and equivalents.

[0017] Referring now to FIG. 1, an example embodiment of a front end accessory drive (FEAD) system 10 is shown, merely for illustrative purposes. The FEAD 10 is preferably mounted to an engine and may include a number of engine drive accessories 18, such as a vacuum pump, fuel injection pump, oil pump, water pump, power steering pump, air conditioning pump, alternator, belt-tensioner, or a cam drive, for example. The drive accessories 18 are driven by at least one endless drive belt 24, which is also engaged with a TVD 26 mounted to a nose 28 of the crankshaft 30. The crankshaft 30 drives the TVD 26 and thereby drives the endless drive belt 24, which in turn drives the remaining engine drive accessories 18 and the alternator 20.

[0018] Referring now to FIG. 2, an example of one embodiment of a TVD 26 is shown for illustrative purposes. The TVD 26 includes a hub 32 operatively coupled to an inertia member 36 by a damper elastomeric member 34 to dampen and/or absorb the vibrational frequencies of the rotating hub 32 and of a crankshaft. The damper elastomeric member 34 and the inertia member 36 may be referred to herein collectively as a damper assembly 44. The TVD 26 may also include an isolator (not shown) to prevent transfer of rigid body mode vibrations of the crankshaft to the FEAD system.

[0019] The inertia member 36 is generally radially concentric about the hub 32 and spaced outward from the hub 32 such that the inertia member 36 and the hub 32 define a gap therebetween. The inertia member 36 (which may also be described herein as a pulley body) has an inner radial surface 38 for engagement with the damper elastomeric member 34 and a belt-engaging portion 40 for engagement with an endless drive belt such as the belt 24 in the FEAD system 10 of FIG. 1. The damper elastomeric member 34 may be press fit or injected into the gap defined between the inertia member 36 and the hub 32 so as to non-rigidly couple the hub 32 and the inertia member 36. The damper elastomeric member 34 may be as disclosed in U.S. Pat. No. 7,658,127, which is incorporated herein, in its entirety, by reference.

[0020] With reference to FIG. 5, hub 100 has a central member 102 having a central bore 104 and an outer radial surface 106. Also, hub 100 has a peripheral rim 108 generally radially concentric about the central member 102 and spaced radially outward therefrom, and a plurality of spokes 110 extending from the outer radial surface 106 of the central member 102 to an inner radial surface 112 of the peripheral rim 108. The hub 100 is mountable to a crankshaft (as shown in FIG. 1) by receiving the crankshaft through its central bore 104. The peripheral rim 108 has an outer radial surface 114 for engagement with a damper assembly, as shown in FIG. 2. The hub 100 may be cast, spun, forged, machined, or molded using known or hereinafter developed techniques, but is more preferably cast or forged. Suitable materials for the hub 100 include, but are not limited to, iron, steel, aluminum, other suitable metals, plastics, or a combination thereof, including composite materials. In one embodiment, the hub is gray cast iron.

[0021] Referring to FIG. 5, the plurality of spokes 110 may include two or more spokes that each have an asymmetrical thickness in an angular direction relative to the axis of rotation A, as evidenced by a cross-section view transverse to a radial length L.sub.R of each of the plurality of spokes. Each spoke 110 has a leading face 122 and a trailing face 124 with opposing radial faces 126, 128 extending therebetween. “Leading” and “trailing” are used herein with reference to the direction of rotation of the hub 100 about the axis of rotation A. The asymmetrical thickness is greatest where the loading effects of the belt torque and dynamic torque are in unison, which is typically more proximate the trailing face 124 of the spoke, and is identified as the trailing width W.sub.T of the spoke. Accordingly, the thickness of the spoke is less more proximate the leading face 122, and is identified as the leading width W.sub.L. As shown in FIG. 5, the asymmetrical thickness or width of each spoke increases from the leading face 122 to the trailing face 124.

[0022] The asymmetrical thickness may increase from the leading face 122 to the trailing face 124 as a mathematical linear function, as a hyperbolic function, or as a parabolic function mirrored at the opposing radial faces 126, 128. As shown in FIG. 5 and FIG. 6A, the increase in the asymmetrical thickness may be according to a mathematical linear function that results in the cross-section having a trapezoidal shape. As shown in FIG. 6B, the increase in the asymmetrical thickness may be according to a mathematical hyperbolic function at the opposing radial faces 126, 128, or as shown in FIG. 6C, may be according to a mathematical parabolic function at the opposing radial faces 126, 128. In other embodiments, the asymmetrical thickness increases from the leading face 122 to the trailing face 124 as a first linear function that changes to a different second linear function mirrored on the opposing radial faces 126, 128 as shown in FIG. 6D. In yet other embodiments, the asymmetrical thickness increases from the leading face 122 to the trailing face 124 as a nonlinear function that changes to a linear function mirrored on opposing radial faces, as shown in FIG. 6E, or vice versa.

[0023] The spokes 110 disclosed herein are designed to withstand the loads applied by belt tension, belt torque, and dynamic torque. Dynamic torque is exerted by the inertia ring in resonance. The dynamic torque is bidirectional, and the belt torque is unidirectional. The torsional vibration damper experiences a greater tensile load where the belt torque and the dynamic torque complement each other compared to where the belt torque and the dynamic torque counteract each other. Brittle materials such as gray cast iron for conventional spokes (those of uniform thickness from the leading face to the trailing face) exhibit varying strengths in tension and compression, e.g., an ultimate tensile strength of 240 MPa and an ultimate compressive strength of 840 MPa. The ultimate compressive strength far exceeds the ultimate tensile strength; thus, the spokes need a greater tensile load in one direction—at the complement of the dynamic torque and belt torque. As explained above, this is accomplished with an asymmetrical spoke design having a greater thickness proximate the trailing face of each spoke, relative to the leading face of each spoke.

[0024] The comparative analysis presented in FIGS. 3 and 4 demonstrates the superior results of the spokes 110 having asymmetrical thickness. FIG. 3 is 3D finite element modeling of a hub having conventional spokes of uniform thickness, and FIG. 4 is 3D finite element modeling of a hub having the asymmetrical spoke design disclosed herein. The 3D finite element modeling in these figures is a representation of a maximum principal stress plot in MPa that has been normalized to 100 MPa for comparison. The maximum value for the conventional spoke in FIG. 3 is 121 MPa, which is indicated by the section of red on the trailing face of the spoke. There is much less red in the 3D finite element modeling of FIG. 4, and the maximum value is 103 MPa. If the hubs of FIG. 3 and FIG. 4 (and hence each TVD comprising the same) have the same mass, the asymmetrical spoke designs herein provide a hub that is nearly 15% stronger under combined belt torque and dynamic torque. If desired, the asymmetrical thickness is one way to actually reduce the mass of the TVDs (by using less material in the spokes) and still have a spoke with the structural integrity to handle the loads discussed above.

[0025] Although the invention is shown and described with respect to certain embodiments, it is obvious that modifications will occur to those skilled in the art upon reading and understanding the specification, and the present invention includes all such modifications.