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- Mar 26, 2018
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So I am about 60-70% done with a PM Research #6 engine and after a long hiatus, I am back into the build. I was thinking through steam engines from an engineering perspective and trying to understand how they differ from gasoline engines. In particular I was curious, if one to design a steam engine from scratch, what decisions could be made to improve the mechanical work done per unit of steam (specific work). Consider the the engine's fuel efficiency.
Here is the PV Indicator Diagram for a real steam engine as it travels through the engine's cycle. My #6 is a double stroke engine, so the return stroke would have a similar diagram but it would progress 180 degrees out of phase from the forward stroke..
This diagram shows the pressure and volume of the working fluid. The area contained inside the curve is the mechanical work extracted from the hot gas. Starting at #1, the piston is at top dead center (TDC) and full of high pressure steam. As the piston begins to stroke forward, we travel to #2. The steam valve does not close immediately so the piston remains at boiler pressure until we pass #2 (valve closing). From there, the gas trapped in the piston decreases in pressure while increasing in volume, driving the piston forward. At #3, the exhaust valve opens and pressure drops from #3 to #4. At #4, the exhaust valve closes and the cylinder retracts under the inertia of the flywheel to #5 where the steam value opens and fills the piston with steam. Once the piston hits top dead center #1, the cycle repeats.
The real steam indicator diagram is drawn as a blue line inside the ideal curve (red). This accounts for the non-instant opening and closing of the valves, valves opening before the end of stroke, and gas being trapped in the returning piston once the exhaust valve is closed.
If we want to extract the maximum work from the engine, we must design it such that the blue line lies as close to the red line as possible. Here are my personal thoughts on what would do this the best, although I could be wrong on some - would love to discuss.
#1) Steam must enter a hot cylinder. Any heat loss to the cylinder walls will drop the curve at point A from ideal as the pressure in the cylinder will decrease before the power stroke can begin.
#2) The steam valve should provide a high flow of steam into the piston (large orifices in the valve). This will allow the cylinder to pressurize as rapidly as possible. This would bring the segment E->A closer to the segment 5->1.
#3) The steam valve should open and close as rapidly as possible and be open for the least amount of time possible. This allows the maximum amount of stroke of the piston to extract work from the gas.
#4) The steam porting volume contained on the cylinder side of the valve should be minimized. This will minimize the volume of steam consumed per stroke. The exhaust pressure of the steam should be as close to atmospheric as possible. Any pressure left in the cylinder at exhaust is waste. This may not be optimal for power output of the engine.
#5) The exhaust valve should open as close to the end of stroke as possible, allowing the maximum time for the gas to expand and do work.
#6) The exhaust valve should remain open for as much of the return stroke as possible. This minimizes the compression of gas as the cylinder approaches top dead center and moves point E closer to ideal.
#7) If there is a minimum cylinder + porting volume at TDC achievable due to mechanical requirements and porting dimensions, then there is a maximum steam supply pressure beyond which any additional pressure adds no work and will be exhausted above atmospheric pressure.
#8) Steam pressure below this maximum pressure may extract more work from the gas (efficiency) at the expense of power output. There is a critical pressure which provides high efficiency and power. Higher pressure = more power, lower pressure = more efficiency (I think).
#9) An optimized steam valve orifice (not just a circular port) could improve the valve response and the efficiency.
#10) An optimized steam valve actuator design could allow for independently adjustable durations of the supply and exhaust segments, and well as rapid transitions between opening and closing.
Here is the PV Indicator Diagram for a real steam engine as it travels through the engine's cycle. My #6 is a double stroke engine, so the return stroke would have a similar diagram but it would progress 180 degrees out of phase from the forward stroke..
This diagram shows the pressure and volume of the working fluid. The area contained inside the curve is the mechanical work extracted from the hot gas. Starting at #1, the piston is at top dead center (TDC) and full of high pressure steam. As the piston begins to stroke forward, we travel to #2. The steam valve does not close immediately so the piston remains at boiler pressure until we pass #2 (valve closing). From there, the gas trapped in the piston decreases in pressure while increasing in volume, driving the piston forward. At #3, the exhaust valve opens and pressure drops from #3 to #4. At #4, the exhaust valve closes and the cylinder retracts under the inertia of the flywheel to #5 where the steam value opens and fills the piston with steam. Once the piston hits top dead center #1, the cycle repeats.
The real steam indicator diagram is drawn as a blue line inside the ideal curve (red). This accounts for the non-instant opening and closing of the valves, valves opening before the end of stroke, and gas being trapped in the returning piston once the exhaust valve is closed.
If we want to extract the maximum work from the engine, we must design it such that the blue line lies as close to the red line as possible. Here are my personal thoughts on what would do this the best, although I could be wrong on some - would love to discuss.
#1) Steam must enter a hot cylinder. Any heat loss to the cylinder walls will drop the curve at point A from ideal as the pressure in the cylinder will decrease before the power stroke can begin.
#2) The steam valve should provide a high flow of steam into the piston (large orifices in the valve). This will allow the cylinder to pressurize as rapidly as possible. This would bring the segment E->A closer to the segment 5->1.
#3) The steam valve should open and close as rapidly as possible and be open for the least amount of time possible. This allows the maximum amount of stroke of the piston to extract work from the gas.
#4) The steam porting volume contained on the cylinder side of the valve should be minimized. This will minimize the volume of steam consumed per stroke. The exhaust pressure of the steam should be as close to atmospheric as possible. Any pressure left in the cylinder at exhaust is waste. This may not be optimal for power output of the engine.
#5) The exhaust valve should open as close to the end of stroke as possible, allowing the maximum time for the gas to expand and do work.
#6) The exhaust valve should remain open for as much of the return stroke as possible. This minimizes the compression of gas as the cylinder approaches top dead center and moves point E closer to ideal.
#7) If there is a minimum cylinder + porting volume at TDC achievable due to mechanical requirements and porting dimensions, then there is a maximum steam supply pressure beyond which any additional pressure adds no work and will be exhausted above atmospheric pressure.
#8) Steam pressure below this maximum pressure may extract more work from the gas (efficiency) at the expense of power output. There is a critical pressure which provides high efficiency and power. Higher pressure = more power, lower pressure = more efficiency (I think).
#9) An optimized steam valve orifice (not just a circular port) could improve the valve response and the efficiency.
#10) An optimized steam valve actuator design could allow for independently adjustable durations of the supply and exhaust segments, and well as rapid transitions between opening and closing.