Cowboy

This is how they're plumbed. And this is kinda a crude drawing of the advantage of compounds. Red is a small turbo, Blue is a large turbo, and purple are compounds. You can see that the compounds don't spool quite as well as the secondary (small turbo) and don't flow quite as well as the primary (large turbo), but the broad RPM band and being able to keep the turbos in there efficiency range is the advantage.

OK Fine, yall get a Mopar1973Man exclusive... Don't tell all the girls where I've been hiding...

I've always used the chart from http://www.innovativebalancing.com I've done a couple dozen with the .177 BB's you get from walmart and don't have any complaints.

Here yar.

17-22 psi idling, 25-35 psi @ 2500 RPM no load is the spec. I got mine at 35-40psi because it gives me the warm and fuzzies.

These diesels can rattle a house down. The pins job is to keep the timing case 'centered' on the block, due to the injection pump and vacuum pump being bolted to the case, if it shifts, the gears will no longer be in alignment with the cam gear which drives them. Because of all the weight hanging off the case with a 50lb injection pump and the engine vibration, it's not unlikely. The handful of bolts holding the timing case to the block are also known for backing off due to engine vibration. So it's a good idea to take them out one by one and red locktite them.

I'd get a new pin, It keeps all the gears aligned properly. '95's came stock with vacuum boost brakes. The connection should be here.

This may help as well:

Postimg.org and imgur.com are my two go-to's for hosting images. I've disliked photobucket from the start.

I have to agree with you John on many points. A part in me really wanted to get all technical about a formula for calculating the post turbine temps. But after reading your last couple posts, reality hit me like a brick and I realized no one is going to grab a calculator while pulling a hill to find if there temps are acceptable. And likewise, no one is watching their boost gauge at 5 psi like in my previous example. So I did a little datalogging while bringin' in the hay the last couple days. Nothing scientific, hard to get nice smooth data on gravel roads. Here's one graph, the X axis is time in seconds. Towards the end of the pull, Pre-EGT's are at 1415, while Post-EGT's are at 981. That makes for a delta temp of 434°F. Boost stayed pretty steady at 35 psi so that's 12.4 Degrees per PSI. And again: At 31.4 seconds: Pre-EGT = 1202°F Post-EGT = 830°F Delta = 372°F Boost ~27.2 psi Degree per PSI = 13.6 And one more. I shifted down this time to try and get the revs a little higher for increased drive pressure. At 14.8 seconds: Pre-EGT = 1147°F Post-EGT = 789°F Delta = 358°F Boost ~25.2 psi Degree per PSI = 14.2 So overall 10°F per psi boost is pretty close. Especially when you're swagging at it with a general rule of thumb. The number does seem to go up with RPM slightly, which makes sense due to increased drive pressure. On "measuring the temperature of the flame coming out of the head" I don't believe that to be necessarily accurate. Pre-turbine temps are 'artificially' (using the word loosely) inflated by drive pressure. Post-turbine temps better indicate the air to fuel ratio, when you're trying to make power at an RPM that the turbo isn't happy with, then it takes a lot more fuel to make the same amount of boost thus like you say John, Post temps can be out of hand, while pre-temps (which arn't being inflated much by drive pressure due to the lack of it), don't indicate anything as being wrong. As for my comment about turbine efficiency. I have always assumed that the inefficiency of the turbine adds heat to the exhaust just like the inefficiency of the compressor adds heat to the intake.... But. I just tried putting together a calculator for it assuming Adiabatic decompression, and well, either I fricked up somewhere, or that's not really the case. It will take more thought at a later date. EDIT: Quick test of my formula using it to calculate pre-IC temperatures puts it pretty accurate... I don't know anymore.

On a single-scroll turbine, I can see the 10° per psi rule of thumb being fairly accurate. But the efficiency curve of a twin-scroll housings are far more dynamic than a single scroll. And in the end, that is what determines pre vs post temps. When the pressure drops over the turbine housing, that causes a temperature drop. But just like the inefficiency of the compressor adds heat to the intake, the same goes for the turbine heating up the post turbine exhaust temps. As an example, I was pulling a grade yesterday, 850°F pre-temps & 650°F post-temps with 5 psi of boost. Another example, pulling a grade at 1900 RPM, 1140ºF Pre-temps & 780°F post temps with 20 psi of boost.

Forgive me if I'm wrong. But Mercedes recommends a 50W fluid. The closest obtainable fluid to their spec is a Mobile Delvac 50 (SAE 50). However It's fairly thick and doesn't shift very well, especially cold. I'm personally thinking on trying a redline product. I'm currently running the CD-50. I've hauled 14k trailer weight running 65 mph and all sorts of other bullshitery and the highest I've seen was 160°F oil temp. At some point I'll be hauling a lot of weight at low speeds, I'm curious to see how it does then.

I did a little data collection as far as pre vs post turbine temps. This is on my 12V'er so your mileage may very. Not as scientific as it could be as the hills were short, and post turbine temps are heavily influenced by heat soak. 1680 RPM @ 860 Pre-EGT = 700 Post-EGT. 1875 RPM @ 1000 Pre-EGT = 740 Post-EGT. 2060 RPM @ 960 Pre-EGT = 720 Post-EGT. 2120 RPM @ 910 Pre-EGT = 710 Post-EGT. 2190 RPM @ 1050 Pre-EGT = 760 Post-EGT. 2240 RPM @ 1250 Pre-EGT = 840 Post-EGT. 2640 RPM @ 1040 Pre-EGT = 735 Post-EGT.

I buddy ran a cheap single ceramic he got off ebay for a while. When I pulled it out, it also had a 13" dual drilled flywheel with HD pilot bearing. So it's not necessarily from SB or Valair. I threw a 13" Organic in in its stead and he couldn't be happier.

Ehh yeah, but you don't get redneck point for that.