lebowski
Part of things
Hillman Avenger, Clan Clover
Posts: 476
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Dec 20, 2006 16:50:04 GMT
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I have a bit of a technical question about dynamic compression ratios and turbo's (and cam's). This article: cochise.uia.net/pkelley2/DynamicCR.htmlsuggests that the optimum dynamic compression ratio for an engine is usually 7.5 - 8.5:1. Now I understand everything written in the article but am wondering what the situation is when a turbo is added to the engine. For example, I have deduced that my engine, with a static compression ratio of 8.5:1, will have a dynamic compression ratio of 6.01:1 with the standard cam that closes the inlet 78 degrees ABDC. If I change the cam to one which closes at 63 degrees ABDC, the dynamic compression becomes 6.85:1. This is the mildest cam I can fit without having one ground. The question is will I gain performance by switching to the milder cam? I know that the dynamic stroke will be greater and therefore less of the air/fuel mix will be pushed out of the (still open) inlet valve. Also, since my cylinders will be more than 100% full (due to the turbo), there will be less (or no) ramming effect with the longer duration cam than there would be with natural aspiration. Therefore, it is my opinion that I'd be better changing to the milder cam. Does anyone with experience in this area agree/disagree? Cheers (Random picture to ease boredom)
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Dec 20, 2006 17:09:47 GMT
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I've looked into this a bit, and have found numerous sources saying that a mild cam is better for turbocharging because of the situation you describe - a long cam overlap will mean some of the inlet charge being blown back out the exhaust. Someone may be able to give you a fuller explanation / shoot me down in flames, but that's how I understand it.
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froggy
Posted a lot
Posts: 1,099
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Dec 20, 2006 19:29:54 GMT
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unlesss you are getting seroius with boost the stock cam is always the best starting point for driveability as the charge air is pressurized and you arent massively going above the normal rev range due to better torque most of the books say the same thing stick with the stock cam
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Dec 21, 2006 11:20:30 GMT
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Its all about overlap. You are leaking charge if the cam has a lot of overlap and thats defeating the object of forced induction. Stock cams designed to minimise emissions are always claimed to work well with moderate turbo applications, but theres nothing to stop you having a custom ground cam with minimal overlap and an extended exhaust opening to minimise pumping losses. Is this an OHC or OHV engine? Would high ratio rockers be an option if its OHV?
I know very little about turbos I'm afraid.
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1937 Austin Street Rod - 1941 Wolseley Not Rod - 1956 Humber Hawk - 1957 Daimler Conquest - 1966 Buick LeSabre - 1968 Plymouth Sport Fury - 1968 Ford Galaxie - 1969 Ford Country Squire - 1969 Mercury Marquis - 1970 Morris Minor - 1970 Buick Skylark - 1970 Ford Galaxie - 1971 Ford Galaxie - 1976 Continental Mark IV - 1976 Ford Capri - 1976 Rover V8 - 1994 Ford Fiesta
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lebowski
Part of things
Hillman Avenger, Clan Clover
Posts: 476
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Dec 21, 2006 11:40:24 GMT
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I realise the point about overlap, but for the moment I'm just talking about the inlets only. The later that the inlet valve closes, the less effective stroke there is left to compress the charge, because the piston starts moving up the bore after BDC. So with a cam that closes the inlets 78 degrees after BDC, that means that the inlet is still open for 78 degrees while the piston is coming up the bore.
If I choose a cam which closes the inlets nearer to BDC, then I believe that less mixture will be pushed out the inlet by the piston, and overall I'll be left with more charge in the cylinder to do work.
However, with the longer duration (78 degree) cam, the turbo can be pushing charge into the cylinders for a longer time, but once BDC is reached, the cylinder is effectively getting smaller. It's kind of like the goalposts are moving, and may have to be a suck it and see situation.
Cheers
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Dec 21, 2006 12:30:57 GMT
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OK I see what you are saying now. A lot of people say IVO/IVC are the two most significant timing events when tuning an engine and that applies as much to N/A as forced indution engines. I know from my own projects that phasing a cam to open 3* earlier or later can make a tremendous amount of difference to how the motor runs, and much of this is due to the relative positins of the piston and the intake valve. Your motor being a turbo does not rely on atmospheric pressure or scavenging effect from the exhaust in order to maximise cylinder fill so if anything surely you have a bit more flexibility to maximise you effective stroke - although this will probably involve a custom ground cam unless you have a common application. Also you're going to want better timing adjustment than a 3 way sproket gives you, I presume you can get some kind of adjustable vernier pulley for your engine? I'd also also have supposed that fully mechanical valve gear would help with the precission here, although you can use a solid tapet to set up hydraulic actuated valves for purposes of setting up but you can't guarantee that a hydraulic is going to operate exactly like that in use...
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1937 Austin Street Rod - 1941 Wolseley Not Rod - 1956 Humber Hawk - 1957 Daimler Conquest - 1966 Buick LeSabre - 1968 Plymouth Sport Fury - 1968 Ford Galaxie - 1969 Ford Country Squire - 1969 Mercury Marquis - 1970 Morris Minor - 1970 Buick Skylark - 1970 Ford Galaxie - 1971 Ford Galaxie - 1976 Continental Mark IV - 1976 Ford Capri - 1976 Rover V8 - 1994 Ford Fiesta
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Dec 21, 2006 12:36:54 GMT
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What you have to remeber is the lag experienced by the air moving into the cylinders, as the air has an effective mass its inertial force will be continuing to push it into the cylinder past BDC. This is how pulse tuning works, using the mass of the air and the pulses in conjunction with the valve timing to create a column of air pusing into the cylinder just as the valve is closing, providing extra cylinder filling. Upto 7 or 8psi can be seen on a well tuned NA engine using pulse tuning. See, now look what you've made me do, ive got all my bloody university notes out now Right, effective ompression ratio also depends on the spark point, this is why retarding the spark works so well compared to lowering the compression ratio. Lowering the compression ratio results in a reduced expansion ratio too, reducing the engines efficiency in capturing heat from the combustion process, if the compression ratio is kept high then more heat can be captured by the piston on the down stroke through increased expansion. Effective compression ratio from inlet closing to spark - = Volume @ I.c. Volume @ spark For an 11:1 generic 1600cc engine (ford sigma / zetec) Volume at spark (30 deg BTDC) ~ 2 Volume at TDC If the compression ratio is lowered with a larger chamber volume from a dished piston or larger combustion chamber for higher boost Volume at spark (30 deg BTDC) < 2 Volume at TDC So if the chamber volume for the 11:1 engine is 35cc then at 30 degrees BTDC the volume will be 70cc. This makes a ratio of 70 / 35 = 2 For the lower compression ratio the TDC volume will be ~ 45cc plus the volume at 30 degrees BTDC (35cc) will equal 80cc. This makes a ratio of 80 / 35 = 1.8 So to compensate for a turbo on a high compression engine the ignition can be retarded. If the ignition is retarded by 10 degrees then the volume in the chamber is smaller prior to combustion commencing, this results in a lower peak pressure due to the piston moving down the bore further as the flame propagates past TDC. So if the chamber volume for the 11:1 engine ~ 35cc plus the volume at 30 degrees BTDC (27cc) will equal 62cc. This makes a ratio of 62 / 35 = 1.77 This is the all important part, is this ratio drops then the compression prior to TDC is lower, meaning the pressure building from the combustion occurs much slower because the piston is moving away from it. Hope this helps Cheers J
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Last Edit: Dec 21, 2006 12:38:21 GMT by Blown_Imp
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DutyFreeSaviour
Europe
Back For More heartbreak and disappointment.....
Posts: 2,944
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Dec 21, 2006 14:01:41 GMT
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I have just read all of that - and am now off for a lie down! You want to give me the theory on Supercharging then? I have a Suzuki Alto - the crank pulley has a spare drive wheel attached for the non-existant power steering and I have a Merc blower........ help me prevent a complete detonation please! ;D Actually - I'll leave that one for another thread. Got the Triooomphs to slam first......
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Back from the dead..... kind of
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Dec 21, 2006 14:16:30 GMT
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Do it GTV, would be ace!! Start a thread and ill do my best, as I'm sure everyone else will too
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lebowski
Part of things
Hillman Avenger, Clan Clover
Posts: 476
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Dec 21, 2006 14:23:19 GMT
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Cheers for the replies. BlownImp, I understand what you're saying and I agree, but I've read in a few places that it may be better to lower compression than to retard ignition when trying to avoid detonation. This is because the location of peak pressure in the cylinder needs to be around 14 degrees ATDC to do maximum work on the piston. The following passages are taken from here if you want to read it all: www.germanmotorcars.com/Detonation.htm"There is another factor that engineers look for to quantify combustion. It is called "location of peak pressure (LPP)." It is measured by an in-cylinder pressure transducer. Ideally, the LPP should occur at 14 degrees after top dead center. Depending on the chamber design and the burn rate, if one would initiate the spark at its optimum timing (20 degrees BTDC, for example) the burn would progress through the chamber and reach LPP, or peak pressure at 14 degrees after top dead center. LPP is a mechanical factor just as an engine is a mechanical device. The piston can only go up and down so fast. If you peak the pressure too soon or too late in the cycle, you won't have optimum work. Therefore, LPP is always 14 degrees ATDC for any engine." "Production engines are optimized for the type or grade of fuel that the marketplace desires or offers. Engine designers use the term called MBT ( Minimum spark for Best Torque) for efficiency and maximum power; it is desirable to operate at MBT at all times. For example, let's pick a specific engine operating point, 4000 RPM, what, 98 kPa MAP. At that operating point with the engine on the dynamometer and using non-knocking fuel, we adjust the spark advance. There is going to be a point where the power is the greatest. Less spark than that, the power falls off, more spark advance than that, you don't get any additional power. Now our engine was initially designed for premium fuel and was calibrated for 20 degrees of spark advance. Suppose we put regular fuel in the engine and it spark knocks at 20 degrees? We back off the timing down to 10 degrees to get the detonation to stop. It doesn't detonate any more, but with 10 degrees of spark retard, the engine is not optimized anymore. The engine now suffers about a 5-6 percent loss in torque output. That's an unacceptable situation. To optimize for regular fuel engine designers will lower the compression ratio to allow an increase in the spark advance to MBT. The result, typically, is only a 1-2 percent torque loss by lowering the compression. This is a better tradeoff. Engine test data determines how much compression an engine can have and run at the optimum spark advance." Now the decision whether to lower compression based on the above statements is dependant on the combustion chamber burn rate of the engine in question (Hillman Avenger all iron OHV in this case). Since I haven't run the engine yet I don't know whether it will suffer detonation or not with the proposed boost levels (12psi at first). However, it has a biscuit shaped combustion chamber which probably doesn't have a very fast burn rate. This means that it would need more ignition advance to burn all the fuel in the chamber, increasing the risk of detonation as the burning fuel has more time to heat up and compress, therefore a lower compression ratio may be required. Phew! I got a bit carried away there. Any more views welcome. Cheers
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lebowski
Part of things
Hillman Avenger, Clan Clover
Posts: 476
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Dec 21, 2006 14:24:46 GMT
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Of course my pumping losses will also be greater by starting the spark earlier. So many things to think about
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Dec 21, 2006 15:01:20 GMT
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Increased burn speed due to better mixture distribution caused by turbcharger turbulence. Decreased burn speed due to increased mixture density. Uneven distribution due to single carb multi cylinder setup. A carb setup that wont be fulling 100% at all times. All iron engine thats prone to detonation due to low thernal conductivity. All of the above affect burn speed, and so your wiebe function changes and so does the peak pressure in the cylinder. What really matters is the area under the graph of your cylinder pressure Vs crank angle, this is what dictates the actual torque output and the amount of energy transferred to the piston. In a turbo engine it dosent matter if the peak pressure moves around a bit due to the fact that the overall amount of pressure normally climbs a but slower and drops slower, making for a 'fatter' pressure curve. The thing to look at is what manufacturers are doing in WRC, most are running high boost high compression ratio engines. These will run perfect timing at lower RPM to make the engine tractable off boost, then as it comes on boost they pull timing out to prevent detonation, then as the restrictor comes into play the timing is put back in again to make more power in the high RPM areas. What kind of biscuits are we talking here? End of the day its not a full on WRC engine, i suggest getting it running and see how it performs. Moving your peak pressure either side of 14 degrees atdc is going to be impossible to calibrate or detect imo (unless you have a sparkplug piezo pressure transducer). You will however be able to detect detonation and remove it by pulling timing out. if it runs tune it, if it dosent run get it running J
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Dec 21, 2006 15:02:14 GMT
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Oh and starting you spark earlier wont incurr a pumping loss, it will be part of your friction mean effective pressure (FMEP)
J
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Dec 21, 2006 15:04:43 GMT
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I have no idea what you're all on about, but I love it and I'm feeling proud to share a forum with you! ;D
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Dec 21, 2006 15:06:30 GMT
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DutyFreeSaviour
Europe
Back For More heartbreak and disappointment.....
Posts: 2,944
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Dec 21, 2006 16:24:35 GMT
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Holy hell! - Just back from a lie down and find that lot! Do we need a visa to visit your planet??? I actually got a lot of it - that's the scary part!
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Back from the dead..... kind of
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lebowski
Part of things
Hillman Avenger, Clan Clover
Posts: 476
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Dec 21, 2006 16:58:09 GMT
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Ok, cheers. The combustion chamber could be likened to a pair of rich tea's sandwiched together I'll probably leave the cam as it is for the moment, with the possibility of changing it for the milder one at a later date. Incidentally, the car will be running on throttle bodies, fuel injection and ignition management rather than the single carb and dizzy, so I'll be able to alter ignition timing as much as I want. Thanks for the comments, anymore welcome.
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Other than the fact this sounds like a wicked project and I look forward to seeing the results, nothing much to add. Other than really I'd be looking at a decent cam optimised for your setup but I think you're right to get it running first and then look at enhancements.
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1937 Austin Street Rod - 1941 Wolseley Not Rod - 1956 Humber Hawk - 1957 Daimler Conquest - 1966 Buick LeSabre - 1968 Plymouth Sport Fury - 1968 Ford Galaxie - 1969 Ford Country Squire - 1969 Mercury Marquis - 1970 Morris Minor - 1970 Buick Skylark - 1970 Ford Galaxie - 1971 Ford Galaxie - 1976 Continental Mark IV - 1976 Ford Capri - 1976 Rover V8 - 1994 Ford Fiesta
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Dec 22, 2006 10:01:49 GMT
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Perfect, with all the injection malarkey!! Get builidin
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lebowski
Part of things
Hillman Avenger, Clan Clover
Posts: 476
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Dec 22, 2006 11:07:47 GMT
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Am doing. It's nearly done now. Just gotta finish making the inlet manifold and wire up the megasquirt really, then fit it all. Got myself a Scorpio in tank fuel pump yesterday. I'll start a proper thread when I've got a few more pictures.
Cheers
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