Jim Storma,
Here are my thoughts on dynamically balancing crankshafts for single-cylinder engines – in summary, it is a waste of time and money. The typical single-cylinder engine inherently has unresolved inertia forces that will cause vibration of the engine structure. The best compromise that can be made (without resorting to complicated, counter-rotating or reciprocating balance masses) is to strive for a 50% RBF (Reciprocating Balance Factor). The mass of the piston assembly and upper end of the con rod constitute the reciprocating mass. The lower end of the rod, crankshaft crankpin and throws, constitute the rotating mass. Ideally, the crankshaft counterweights are sized such that their mass counterbalances the rotating mass by 100% and the reciprocating mass by 50%. This results in the least amount of transmitted vibration into the engine structure, and in turn, into the surrounding vehicle.
These K-series engines were typically underbalanced – that is the RBF is around 27%. Reasoning is twofold:
1) Underbalancing allows the engine to shake more along the vertical (cylinder) axis. Vibrational forces oriented in this direction are felt less by the operator in a vehicle application such as a tractor.
2) The K-series engines are fitted with balance gears for certain applications. These balance gears effectively increase the RBF to 50%.
The balance gears have proven unreliable in high-time engines and when they fail, they usually cause severe damage to the engine block. The general consensus is to remove them and live with slightly increased vibration.
There are ways around this, however. You can drill the counterweights and install tungsten plugs (heavy metal) or buy a counterweight plate from me that will substitute for the balance gears and restore the 50% RBF. Another thing to be aware of is the mass of the piston assembly. If you are rebuilding your engine and using aftermarket parts, beware of the increased mass of the piston and especially the wrist pin, when compared to the OEM (Original Equipment Manufactured) parts. I’ve found that the Stens pistons are close to the OEM Kohler part, but the wrist pin is almost double the mass of OEM! The aftermarket pin has very thick wall section, whereas the Kohler pin is quite thin. It is the mass of the recip assembly that is the principal generator of these recip inertia forces and must be kept as light as possible. I advocate reusing the Kohler pin in the new piston after you measure everything up and check that it will fit dimensionally.
Assuming the engine is now at the 50% target RBF, will it run as smoothly as an opposed-6 or V-8…absolutely not! There are still going to be unresolved forces that will cause vibration, but the engine will be perceived to be smoother just because these internal forces have been minimized, thus reducing the vibrational amplitude. Now you could take the crankshaft to a balance shop and instruct them to dynamically balance the assembly to a 50% RBF. This would entail making up a correctly sized bobweight to affix to the crankpin, spinning up the crankshaft, and removing or adding metal where needed. This may alter the RBF by 1 or 2%, but this small change would have almost no effect on the total transmitted vibration from the running engine. As a matter of fact, there is no discernable change in vibrational amplitude felt by the tractor operator if the RBF varies from 45 to 55%. This is why I feel that dynamically balancing crankshafts for these engines is just a waste.
Hope this hasn’t been too long winded. This is a moderately complex subject that I’ve hopefully hit on all the key issues.