Supercharged Four Wheel Drive Ford Mondeo ST220

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Supercharged Four Wheel Drive Ford Mondeo ST220

  1. 1. Supercharged Four Wheel Drive Ford Mondeo ST220 Jon Marchant I should have written this as an open project log from day one but alas I couldn’t be bothered at the time and never thought it would go this far. So, here we are in October 2009… Project goals More power and torque Aiming for 350Bhp. Have read of an intercooled Procharger supercharged ST220 on one of the ST owners club forums that was alleged to develop 321Bhp at the flywheel with only 6 Psi boost pressure. So this became the bench-mark. Additional fuelling on this car achieved with a booster fuel pump and a ‘digital FMU’ which is essentially a manifold pressure sensing fuel pump controller – the FMU increases the speed of the in-line booster fuel pump according to measured boost pressure thereby increasing the fuel rail pressure, causing the injectors to deliver more fuel. Sounds simple, although very crude. Long-term plan, four wheel drive conversion Theoretically possible as in 1994/1995 a 4x4 version of the Mk1 Mondeo was produced in limited numbers with the 2 litre Zetec-E engine. The drive train layout, fuel tank and rear axle assembly ‘should’ be compatible as the floor pan remained essentially unchanged in the Mk2 and Mk3 models. A 4x4 version of the Jaguar X-type 3 litre sport also exists with an engine derived from the Ford Duratec 30 and with a bodyshell and running gear developed from that used in the Mk3 Mondeo.
  2. 2. Start date: April 2008 Initial Modifications: • Eibach lowering springs, 25mm drop, later settled to approx 40mm total drop, improved appearance of car, slightly harder ride, slightly sharper turn-in and more feedback through steering. Not good over speed bumps and have to be careful reversing as exhausts are now low enough to hit a tall curb. • Miltek cat-back exhaust system, improvement on the standard exhaust system in terms of gas flow and exhaust note, deeper and slightly louder. Improved low-mid range torque noticeably and increased fuel economy by around 1- 2mpg! • Focus ST front brakes, much sharper and less susceptible to fade compared to the poor standard Mondeo brakes. Front brakes are a straight swap but the rear calipers are not. Previously tried EBC grooved discs and ‘red stuff’ ceramic pads, the pads were good, little warm-up required and no fade but the discs were crap. The grooved discs made a strange whirring noise from the pads dragging over the grooves even when not braking. This was only noticeable at low speed with the windows down but still louder than the exhaust. Discs also ‘warped’ within 6 months. Standard Focus ST discs and pads ok so far. More Power!!! Having already carried out some investigation into forced induction tuning the ST220’s Duratec 30 V6 engine the following was considered (bearing in mind that my knowledge has developed with the project so at this point I was still very ‘green’):
  3. 3. Turbocharging Favoured for overall efficiency and outright power as well as the potential for a lot of mid-range torque if the turbo/engine combination is well matched. Good for the ‘shove’ factor due to the torque, making the car ‘feel’ faster. Ideal would be a twin turbo set-up with turbochargers sized small enough to minimise lag but the total output of the two enough for good top end power. Discounted due to lack of space in engine bay, as well as the complexity and cost. Then considered a larger single hybrid turbo such as a T04E, this should just fit in the space in front of the gearbox but would necessitate relocation of the battery to the boot and some ‘interesting’ exhaust and induction pipe-work. This seemed like a good idea and indeed there is a company called Nautilus Performance in the US who manufacture a kit for the Ford Contour (Mk2 Mondeo) 2.5 V6, a good starting point for ideas, but… Further investigation suggested that to achieve 350+ Bhp would require 10+ Psi of boost pressure and lowering of the static compression ratio from the standard 10.0:1 to something more like 8.5:1 as well as forged pistons and forged connecting rods – not a cost I thought could be justified at the time. On top of that there would likely be significant lag due to using a larger-ish turbo resulting in a sharp increase in torque when the turbo starts to develop useful boost, this would certainly provide the desired ‘shove’ but at the expense of low speed driveability and shock loading of the clutch, gearbox and suspension. Then there is heat management to consider, the turbocharger as well as its associated exhaust pipe-work will be running very hot and any adjacent components will need adequate heat shielding in an already cramped engine bay. Turbocharging was starting to appear less attractive or at least less practical in this application.
  4. 4. Supercharging Positive displacement superchargers were considered due to the good low-speed torque characteristic but then quickly ruled out due to lack of space. Any supercharger by design has to be driven by the engine and the only useable power take off is from the auxiliary drive belt, which limits the locating options for superchargers considerably. PD superchargers are physically relatively large and as the ST220 has a rather cramped engine bay there is no space available to the front or rear of the engine so the supercharger would have to fit on top in the conventional position. But again there is little space available, not unless a large power bulge is incorporated in the bonnet. Next on the list was centrifugal superchargers like the one used in the bench mark supercharged ST220. Centrifugal superchargers use a centrifugal compressor of the same type as turbochargers, the main difference being that they are not driven by an exhaust driven turbine but by the engine through a step-up gearbox from the auxiliary drive belt. Centrifugal superchargers share turbochargers’ high adiabatic efficiency meaning that they generate less heating of the charge air during compression when compared to a positive displacement supercharger. In addition to this they do not heat the charge air by heat soak from a hot, close-coupled exhaust turbine like turbochargers do. This potentially means overall the charge air will be cooler and have a higher density than with a turbo set-up at the same boost pressure so more power can be developed with less boost pressure. Centrifugal superchargers are also relatively more compact than PD superchargers.
  5. 5. Unfortunately like a turbo, centrifugal superchargers also need to be running at high speed to produce any useful boost pressure, which is why centrifugal superchargers all use some form of step-up drive to increase the speed of the engine to something more useful at the compressor wheel. This in itself is not a problem but in addition all fixed drive superchargers are engine speed dependant and there is a limit to how fast the supercharger can be driven. Therefore at low speed there is little or no boost available but increases steadily up to the engine rev limit. Typically a centrifugal supercharger that is set up to develop 8 Psi boost at an engine speed of 7000 Rpm will only develop 2-3 Psi at 3000 Rpm, a bit like having a large turbo with lots of lag then a very smooth on-boost transition. Technically this is very desirable as the load on the clutch, gearbox and suspension is minimised, there is much less chance of wheel spin and torque steer and the engine sees highest boost pressure when it is most able to handle it – at high speed. Probably not as much fun though… In theory a centrifugal supercharger coupled with some form of variable drive would be the best solution. The variable drive would have a higher step-up ratio at low engine speed to give the required boost pressure then progressively decrease with increasing engine speed to maintain the boost pressure at much the same level without leading to over-boost or over-speeding the supercharger. Paxton Superchargers in the US did this back in the 50s/60s using variable pulley v- belt drives and variable ball drives. At this time I believe there is a company developing multi ratio planetary drives for use with Rotrex centrifugal superchargers. Variable pulley drives were again ruled out due to lack of space around the auxiliary drive belt area but still like the idea.
  6. 6. Another possibility is hydraulic drive. Whereby a hydraulic pump is driven from the auxiliary belt which in turn drives a hydraulic motor, coupled to the input shaft of a centrifugal supercharger. If the flow rate of the pump is higher than that required by the motor for a given rotational speed then a step-up drive relationship can exist, this could then be varied electronically using a proportional control valve to control the hydraulic fluid flow rate and bypass the excess. I liked this idea a lot because it potentially means more low-speed boost pressure and proportional electronic control is possible, it also frees the supercharger from the constraints of having to be located where it can be driven by the auxiliary drive belt as the only connection to the pump would be hoses. Also the only component needing to be driven by the auxiliary belt would be a relatively small hydraulic pump, which should be fairly easy to accommodate. I pursued this idea with Parker Hydraulics, specifically their hydraulic fan drive systems for some time but was eventually told their motors were not capable of running as fast as first suggested. Then I started having doubts that the benefits would outweigh the cost and complexity, not that complexity is necessarily something to be scared of. So, it was decided to just go along with the conventional set-up for the time being. The conventional set-up for centrifugal superchargers is fixed ratio belt drive. The required engine airflow and boost pressure for the desired power output is calculated, then that point looked up on the supercharger compressor map, the required impeller speed is then read-off. This is the target speed for the supercharger’s compressor wheel when the engine speed hits the desired shift point or otherwise at the engine rev-limit. Working backwards the required drive pulley sizes can be calculated. For my target 350 bhp, the boost pressure required would be around 8 psi. This calculation alone does not take into account the effect of adding an intercooler into the system, which can be very significant as I later found out to my cost.
  7. 7. Suitable centrifugal superchargers: • Rotrex, European manufactured, very compact, neat design and much smaller than other comparable centrifugal superchargers but also significantly more expensive. • Paxton, US manufactured, internal synchronous belt step-up drive, lower step- up ratio than other comparable units. • Procharger, US manufactured, fairly common, second-hand units occasionally appear. • Vortech, US manufactured, as with the Procharger units, fairly common and second-hand units occasionally appear. All the US manufactured units seemed to be similar in specification and size but when I came across a suitable second hand Vortech V9F supercharger in need of a re-build, the choice was made for me.
  8. 8. Fuel and Ignition There is also the issue of ECU recalibration. Simple, piggy-back controllers such as the digital FMU were discounted at this point as further research highlighted just how far from ideal these systems are and more importantly that they are not fail-safe. A failure of such a system will result in no additional fuel being supplied under boost causing a lean condition, leading to detonation and potentially serious engine damage. So recalibration or ‘re-mapping’ of the OEM ECU is the way to go for accurate correction of fuelling and ignition. Fitting an after-market ECU was considered for all of 5 minutes until I realised how insanely expensive most are, also the OEM ECU controls not just the engine but also other functions such as the ESP and AC, which I did not want to lose. So I set about locating and contacting tuning companies in the South East who could carry out the necessary re-calibration. Not wanting to slate the industry I did make a few observations. A lot of tuning companies do not carry out any actual tuning, fitting aftermarket exhausts, induction kits, stereos etc. are the kind of thing you should be able to do yourself competently if you drive a ‘tweeked’ motor and do not really constitute ‘tuning’. There also seem to be quite a few tuning companies that only deal with diesels and/or will re-program your car’s ECU with a pre-programmed map from a hand held programmer developed by a proper tuning company. With a little more research I came across Dreamscience who were marketing a re- packaged version of the SCT - XCAL3 with a pre-programmed map they had developed for the standard and mildly modified ST220 and provision for custom re- mapping. I contacted Dreamscience regarding custom re-mapping of my ST220 with a supercharger fitted and they referred me to one of their master dealers who had experience with custom mapping forced induction modified Fords and a good reputation. The company in question is Performance 3000 in Yeovil, Somerset. When contacted they were helpful, and indicated that they would be able to carry out the required re- mapping and provided a quote.
  9. 9. Fitting the Supercharger With a company located who could carry out the ECU re-mapping, work was underway to fit the already rebuilt supercharger. Another plug: Kent Bearings, St leonards-on-sea, East Sussex. Very helpful sourcing suitable replacement high-speed bearings and seals for the supercharger. There were some re-build kits available on Ebay for my supercharger, one of which was actually included with the unit I bought but was a completely unsuitable. The high speed bearings were just bearings that happened to be the correct size but were not rated for high speed use at all and would have quickly overheated and seized! Most of the research into suitable supercharger location took place before purchasing the unit but it was very difficult to be sure without actually offering the supercharger in the engine bay to see where it would fit. The standard ST220 engine bay before modification
  10. 10. And a close-up of the area around the auxiliary drive belt
  11. 11. In the late 1990s Vortech offered a supercharger kit with one of their V9 units for the Ford Contour V6, the US version of the Mk2 Mondeo 2.5 V6. This kit located the supercharger to the gearbox end of the engine towards the front and used a shaft to take drive for the supercharger from the auxiliary drive belt and across the front of the engine to the supercharger. This worked, but not for long… They encountered several serious failures of the drive shaft assembly and withdrew the kit from sale. A redesigned kit was later marketed but was very short-lived and I could not find one. I did look into copying the layout of the Vortech kit but with more research it began to look impractical as the Mk3 engine bay is different to that of the Mk2 and the Contour. This arrangement also necessitated relocation of the battery to the boot as with the turbo kits. For some reason I had a real problem with the idea of relocating the battery at the time, although have since moved just about everything else. I then came across another company in the US who were developing a supercharger kit for the Contour using a Vortech V9 (3lduratec.com). At the time they were not offering any kits for sale but had successfully developed some prototype vehicles. Looking at the pictures of their prototypes, it looked as though the supercharger would also fit in this location in my ST220 with a little modification. 3lduratec.com Ford Contour supercharger location The supercharger is fitted to a very tidy looking bracket, which in turn is fixed to the studs on the top of the upper engine mount bracket.
  12. 12. A neat idea but it does look like the bracket would flex under load as no bracing can be seen in the picture, the routing of the belt drive is also not too obvious. After looking at the above picture for a while it seemed fairly obvious to make the supercharger bracket part of the upper engine mount. In the end I came up with what is shown below. Note some of the following pictures were taken during build and others after (the ones I forgot), so are not necessarily in chronological order. Bracket fabricated from stainless steel plate The induction system progressed from here on a ‘wherever it’ll fit’ basis
  13. 13. Combined MAF and IAT (air mass flow and charge air temperature) sensor retained in original position Bypass valve assembly, the blue one is a dump valve for relieving boost pressure when transitioning off-throttle, which prevents compressor stall and reduces load on the bearings. The purple valve is a modified version of the same dump valve and is configured for pressure relief to limit maximum boost pressure (if required).
  14. 14. Bypass valves in position Bypass valves re-circulate air back to supercharger inlet
  15. 15. The screen washer tank and pumps had to be relocated from in front of the driver’s side front wheel to in front of the gearbox. The coolant header tank also had to be relocated Some of the AC hoses also had to be moved and modified to accommodate the supercharger intake duct. There are very few people who want to help with any sort of modification to vehicle AC systems, lesson learned, en evil to be avoided if possible which unfortunately it wasn’t in this case.
  16. 16. Supercharger power take-off pulley – 2 power steering pump pulleys modified to fit back to back. I did consider the additional radial load on the power steering pump bearing, but as the belts will be pulling away in nearly opposite directions, thought this would semi-cancel. Custom supercharger drive pulley with one-way sprag clutches fitted to allow supercharger to wind down gently during off-throttle transition rather than be forced to slow by drive belt. Reduces reverse-load on belt drive, which is designed to transmit power in one direction only. Incidentally the alternator is fitted with a sprag clutch pulley as standard.
  17. 17. A spring loaded dynamic belt tensioner could not be accommodated due to lack of space so had to opt for an adjustable lever tensioner arrangement. View showing belt run around pulleys.
  18. 18. In addition to the modifications shown above a higher flow fuel pump was fitted along with higher flow injectors to cater for the increased fuel requirements of the supercharged engine. The high flow fuel pump was purchased from PumaSpeed, advertised as a Focus RS (MK1) up-rated fuel pump good for 500 Bhp, this lasted 2 weeks and failed while driving through town on my way home from work. The pump had failed open circuit for apparently no reason so was returned for warranty replacement. I can’t remember the size of the standard injectors, think they were something like 24 lb/hr @ 3bar, the replacement injectors are Ford racing ‘Blue Giant’ (Bosch 0280 156 127) 39 lb/hr @ 3bar which have been flow tested to 42 lb/hr @ 3bar (441 cc/min). These will flow 52 lb/hr (543 cc/min) at the ST220’s fuel rail pressure of 4.5 bar and be good for well over 400 Bhp. Due to changing the injectors the ECU’s basic calibration is now incorrect and as a result injects way too much fuel so the engine will not start or run any sense and is now un-driveable at this stage.
  19. 19. Re-mapping: September 2008 After much work the car was ready to be re-mapped and after pulling a few favours the car was towed down to Yeovil. About half way through the second day of mapping I’m informed that the supercharger is not producing nearly as much boost as expected, struggling to reach 4 Psi, let alone the desired 8 Psi, but as I needed to be able to drive the car back home, suggested that the mapping continue. Meanwhile I re-did all the calculations and could not find anything wrong, the only factor not accounted for was the flow restriction caused by the intercooler. The intercooler was sized so that the end-on flow area of the core was just over double the area of the incoming and exiting pipes and pressure loss was not expected to be more than 1 Psi max. I was then informed that the MAF sensor had maxed out or ‘pegged’ at around 5000 rpm and above this point the engine was starting to run lean. The standard MAF sensor was too sensitive and hit its maximum output voltage at 5000 rpm, well before the rev limiter at 6900 rpm. The only solution was a larger flow MAF sensor and as I also had to find out why the supercharger was not producing the expected boost pressure, the car was mapped to run safe with the rev limiter reduced to 5500 rpm so I could drive it home, disappointed. When home I looked at the numbers trying to understand how I’d got it so catastrophically wrong. Maxing out the MAF sensor was always going to be a risk but was surprised it happened so low in the rev band with so little boost pressure. Producing such low boost pressure was not expected though. Everything seemed correct so I fitted 2 boost pressure gauges, one at the supercharger discharge and another to the inlet manifold and went for a drive. The supercharger was producing the expected boost pressure but this was not reaching the inlet manifold. Was it the intercooler, the throttle body, the convoluted bends in my pipework? I took the intercooler out and replaced it with a straight section of tube and went for another drive: zero pressure loss, it was all down to the intercooler, the engine was now also much more responsive as well and generally felt much nicer to drive. However above 6 Psi boost pressure it is generally recommended that an intercooler is used to keep the charge air temperature down or limit boost pressure, so an intercooler had to be fitted. . The intercooler used was a relatively cheap universal fit one sourced from Ebay. It looked good enough though, high-flow bar and plate construction, decent size, rounded end tanks, although the inlet and outlet hose connections were a little restrictive. The end tanks and hose connections were single piece castings welded onto each end of the core. The hose connection O/D was 2.25”, the rest of the pressurised part of the induction system is 2.5”, but the I/D was only around 2.0”.
  20. 20. To improve this the hose connections were cut off and some larger I/D connections welded on and the intercooler re-fitted. This did make a significant improvement - it had now gone from a 45% pressure drop to around 30%. A larger MAF sensor also had to be sourced and fitted and I’d also been advised to relocate the MAF to the supercharger intake side so that air is being drawn through rather than forced through under pressure. This is supposed to result in greater accuracy and reliability as some MAFs do not like operating under pressure. After some research a new 90mm MAF as fitted to a Ford F150 Lightning was sourced again through Ebay. These are larger than the standard ST220 MAF (90mm as opposed to 75mm), pin for pin compatible except for the omission of the integral IAT sensor and designed for much higher airflow as they are normally fitted to a 5.4 litre supercharged V8! Relocating the MAF upstream of the supercharger did also entail fitting of a separate charge air temperature (IAT) sensor in the original MAF sensor location so that the actual charge air temperature is measured from the air entering the inlet manifold after compression and intercooling. The standard ST220 MAF sensor has its own integral IAT sensor. A Ford Explorer IAT sensor was sourced for this purpose as they are cheap from Ford and testing revealed have the same temperature/resistance relationship as the IAT thermistor integral to the standard ST220 MAF.
  21. 21. 89mm (3.5”) diameter supercharger intake As for getting the boost pressure back up to the level desired, I attempted to calculate how much the supercharger discharge pressure would have to be increased to obtain the desired 8 Psi at the inlet manifold but struggled as the pressure drop across the intercooler did not appear to be fixed. It was decided to simply alter the supercharger pulley size so that the supercharger would run up to its maximum allowable speed and let the boost pressure limiting valve do its job as required – I had originally been advised against trying this but was now willing to take the risk as it seemed likely there would be little excess pressure (airflow) to re-circulate. I had also now been advised that the engine could probably run up to 10 Psi boost without problems due to the low charge air temperature. The max operating speed for the Vortech V9 supercharger was quoted at 62,000 rpm impeller speed by the manufacturer but later de-rated to 55,000 rpm. I opted for a supercharger speed of 56,000 rpm at an engine speed of 6900 rpm as this is the long-term limit of the high-speed bearings used during re-building the supercharger and so another custom pulley was manufactured.
  22. 22. Re-mapping: April 2009 Ready for another try, the rev limit was lowered to 5000 rpm using the XCAL 3 ‘user adjustable options’ the boost limiter valve set to full relief by removing the spring and to be on the safe side, the tank filled with premium 98 RON for the trip down to Yeovil. On arrival at Performance 3000 the spring was re-fitted to the limiter valve and the new MAF and IAT sensors plugged in (the original MAF sensor had to be used for the drive down). Then mapping commenced. The initial set-up went well and the car was soon running correctly with the new MAF and IAT sensors, the new MAF had a lot more headroom than the original and the supercharger was producing significantly more boost pressure at lower engine speed. Mapping then progressed and was looking good until half way through the second day when problems were encountered at around 5000 rpm under load. It seemed almost like the onset of detonation but could not be remedied by retarding ignition timing or increasing fuelling to reduce burn temperature. The charge air temperature was also very low, far lower than would normally be required to contribute to the onset of detonation. Turned out that the engine was misfiring. I forget the name used to describe it but the spark plugs were breaking down and arcing through the side of the ceramic insulators into the HT lead caps. My understanding is that the insulating effect of the fuel/air charge in the cylinders under pressure at high engine load increases the breakdown voltage of the spark plug gap to a point where the plug if weak, can breakdown elsewhere, in this case through the side of the insulators and into the HT lead caps and presumably then into the cylinder head which is the nearest ground. This was evidenced by small black pin marks around the spark plug insulators towards the top. The plugs and leads could not hack it but conveniently I had a new set of standard leads in to boot so new plugs were ordered in for the next morning and once fitted this cured the problem. Mapping continued but then it seemed that the boost pressure was topping out at around 6 psi and would not rise further. The limiter valve was wound fully shut, this improved but did not solve the problem so the dump valve was also wound fully shut and boost pressure continued to rise. This then caused another problem though as it was found that the supercharger shifts enough air at idle that with the throttle shut the pressure rises enough for the compressor to stall causing rapid cyclic airflow reversal back through the supercharger and into the MAF sensor, the output of which was looking rather like a triangle wave. This totally screwed up the mapping at idle and was un-resolvable through further calibration/mapping. The solution was to rip out the original diaphragm dump valve and fit a decent Bailey piston dump valve.
  23. 23. Mapping once again resumed but the engine still seemed to be struggling to get enough air approaching 6000 rpm. Removal of the air filter was tried but settled for simply removing the pre-charger screen from the cone filter as this noticeably increased the airflow but still not enough. The pressure differential across the intercooler was observed to be quite high so a much larger intercooler dug out of the stock room and trial fitted. This instantly freed up another 20 bhp and oddly did not hurt the throttle response as expected. At this point the car was now developing 300 bhp at the wheels at 6100 rpm and assuming approx 17-20% transmission loss is already meeting my target with another 900 rpm or so to go, but then as mapping continued another problem arose. Power output good at 6100 rpm then suddenly falls off very sharply with MAF, IAT and boost pressure remaining constant. Some head scratching ensued but collectively decided that the exhaust system most notably the catalytic converters is limiting gas flow out of the engine and likely causing a sharp increase in exhaust back-pressure and exhaust gas temperature (EGT) above 6100 rpm. So, back home for some more work. During the drive home it was discovered that the rev limiter was for some reason not functioning, an issue that has still yet to be resolved. Below is one of the later dyno print-outs, this one cut short at 5972 rpm but already showing a power output of 292 bhp measured at the front wheels.
  24. 24. Further Development Back home the new larger intercooler and dump valve were properly installed. The boost pressure limiting valve was also removed and replaced with a proper external wastegate as used in high power turbocharger installations. The wastegate has a much larger diaphragm and spring than the weak modified dump valve and so much more capable of holding the boost back without creeping open. The wastegate, like the pressure relief valve, is fitted only as insurance against the remote possibility that the supercharger does eventually produce more boost pressure than desired. The wastegate will most likely not be required and if so, will be removed after further re-mapping. With larger intercooler fitted
  25. 25. New dump (bypass) valve fitted Wastegate valve
  26. 26. The Engine After some discussion it was decided to try source some forged pistons and connecting rods as the engine was already making good power and is not yet done. Nobody seems to be able to advise just how much the standard ST220 engine bottom end can handle, but everybody agrees that the standard sintered rods are a liability. It is expected that freeing up the exhaust system should allow the engine to develop significantly more power beyond 6000 rpm. Normally with centrifugal supercharger set-ups the engine power output rises steadily all the way up to the limiter as there is usually no drop off in supercharger output unless it is too small for the engine’s airflow requirements. Reference back to the compressor map for the V9F supercharger indicates there is plenty more airflow available so the supercharger should not be a limiting factor here. Research revealed that although forged K1 Carillo rods are available for the Duratec 30 engine, the only forged pistons available are low compression ratio 8.5:1 perfect for higher boost pressure applications such as high output turbocharging. This rather made me wish I’d gone with the turbocharging route in the first place as this is a major cost I had not banked on with supercharging. As this is a relatively low boost pressure application, the static compression ratio can be kept reasonably high and did not want to lose low down torque and power throughout the rev range by lowering the compression. To maintain the standard compression ratio of 10.0:1 the only option is custom forged pistons at even higher cost. Custom forged Wiseco pistons and forged Carillo rods ordered from Flatlander Performance 20/08/2009 on a 6 week lead-time.
  27. 27. Four Wheel Drive While waiting for the pistons and rods to arrive, work on the exhaust system could take place but it seemed sensible to first make some headway with the rear axle and fuel tank part of the 4x4 conversion so the modified exhaust system could be routed in sympathy rather than re-routing it again later. The major components of the 4x4 system from a low mileage Jaguar X-Type 3.0 sport had been purchased at the right price and sitting idle for some time. The parts included the gearbox, transfer box, front driveshafts, propshaft and the rear sub-frame complete with all running gear. A fuel tank from a 1995 Mondeo Si 4x4 was also sourced at a later date.
  28. 28. Fuel System The first job was to fit the 4x4 fuel tank. The 4x4 tank is of the ‘saddle’ design where the normal large single fuel tank is effectively split into 2 separate tanks by a transmission tunnel and has a large bridge running over the top. This necessitates the use of 2 fuel pick-ups. The fuel pump and fuel level sender reside in much the same position as for the standard tanks except there is now an additional pick-up and sender assembly on the other side. Fuel is siphoned over from the second pick-up by a valve and t-piece fitted in the main fuel pump return line. By this time the replacement fuel pump from PumaSpeed had already failed in the same manner as before!!!? After some discussion with PumaSpeed the pump was returned for credit, which I did receive after 3 months of chasing! So, another fuel pump was needed and the only standard size high-flow pump I could find that would fit in the new fuel tank (or indeed the original tank) was a Walbro GS342 high pressure 255 litre/hour pump. By my calculations I need up to 195 l/hr @ 4.5 bar but the Walbro pump will not deliver this flow at such a high pressure. An additional pump was needed. Following advice from Performance 3000 I looked into the Bosch 044 inline fuel pumps. These will flow 300 l/hr at up to 5 bar. I now have the Walbro 255 l/hr high-pressure pump in the tank as a lift pump and the Bosch 044 pump along with an adjustable pressure regulator and fuel filter mounted inside the rear of the boot. I still have reservations about the location of the Bosch pump due to noise in the cabin, something yet to be resolved.
  29. 29. The Mk1 Mondeo 4x4 saddle tank thankfully fitted straight where the original tank sat but the rear mounting points for the retaining straps had to be moved further apart as one strap actually ran through the tunnel. I ended up welding lugs onto the rear subframe for this purpose and also lengthening the straps. The Mk1 filler neck also had to be used as the ST220 filler will not fit the Mk1 tank. The in-tank pump/sender assembly with the Walbro pump fitted The transfer pick-up/sender assembly
  30. 30. The main fuel pump, pressure regulator and filter inside the boot The evaporative emissions charcoal canister also had to be relocated behind the trim inside the boot due to lack of space around the rear axle where it originally resided.
  31. 31. Mk3 Mondeo (ST220) OEM ‘return-less’ fuel system To fuel rail Filter Fill Pump Reg Fuel tank Pump/sender assembly MK1 Mondeo 4x4 saddle tank OEM fuel system To fuel rail and regulator Feed Return Fill Siphon valve included within pump/sender 1 assembly Siphon valve Tank Pump Tunnel Pump and sender 1 Pick-up and sender 2
  32. 32. Modified 4x4 saddle tank high flow/pressure fuel system To fuel rail Filter Regulator Swirl pot Main pump Fill Siphon valve included within pump/sender 1 assembly Siphon valve Tank Pump Tunnel Pump and sender 1 Pick-up and sender 2 Standard 4x4 fuel system modified with addition of: • Walbro 255 l/hr high pressure pump as lift pump • Swirl pot to reduce chance of main pump drawing any air • Bosch 044 high flow, high pressure main pump • Adjustable external fuel pressure regulator
  33. 33. Simplified 4x4 saddle tank fuel system without swirl pot To fuel rail Filter Regulator Main pump Fill Siphon valve included within pump/sender 1 assembly Siphon valve Tank Pump Tunnel Balance Pump and sender 1 Pick-up and sender 2 line Swirl pot removed as found to be serving no useful purpose. When the lift pump draws air it appears to ‘airate’ the fuel in the swirl pot so the main pump draws fuel with air bubbles in and cavitates causing a drop in fuel pressure and the pump to run hot. Balance line added connecting bottom of both sided of tank to allow fuel levels to equalize under gravity.
  34. 34. 4x4 Saddle tank fuel system with pumped crossover (triple pump system) To fuel rail Filter Regulator Main pump Fill Tank Pump Tunnel Pump Pump and sender 1 Pump and sender 2 Balance line does not work very effectively and proved difficult to accommodate around exhaust and quite vulnerable so removed. Siphon transfer also does not seem to work all that well so opted for a pumped transfer using and standard fuel pump and sender assembly in place of the existing transfer pick-up and sender assembly.
  35. 35. At free-flow the transfer pump ‘should’ pump fuel over as fast as the lift pump can pump it out. There ‘should’ always be fuel returning to this side of the tank so the transfer pump ‘should’ not run dry. Yet to be proven… Subject to flow testing, the noisy gerotor-type Walbro 255 l/hr lift pump may be removed in favour of the standard ST220 turbine-type pump, which is near silent. It is believed at free-flow this pump should be able to deliver sufficient fuel to the Bosch pressure pump.
  36. 36. Rear Axle Then work began on the rear axle. The Jaguar X-Type rear sub-frame and suspension is based on the Mondeo estate rear as this better accommodated the drive components and increases boot space (for golf clubs) as the springs are under the car much like the Focus ‘control blade’ set-up. This negated the use of the Jaguar rear sub-frame as the rear of the car is totally different and it would definitely not fit without serious modification to the rear of the bodyshell. I looked into the Mondeo Si 4x4 rear axle but these are very rare and most have seen high mileage service. While the sub-frame looked like it could be a straight swap-in fit, the differential is much smaller the than the Jaguar unit already purchased so wondered if the existing ST220 rear sub-frame could be modified to accept the Jag diff. After swapping a few parts around to see what would fit, it appeared that as suspected the Jag and Mondeo rear track was almost exactly the same width and the rear hubs were interchangeable. There were a few obvious issues like the different rear ABS/ESP wheel sensors and the anti-roll bar ends being in the way but nothing un- resolvable. The ST220 rear sub-frame was removed and the Jaguar differential and driveshafts offered up to see if it could all be made to fit. This turned out to be a lot easier than first thought but think there will be ongoing issues with clearance between the underside of the sub-frame and the outer ends of the rear driveshafts in the areas circled below.
  37. 37. This fabrication work was carried out on a proper flat metal workbench in a suitable workshop – not on the picnic bench on which the frame is pictured. During modification of the subframe, additional strengthening was welded in to replace the material removed and overall geometry maintained.
  38. 38. The rear subframe once modified was sent away for Zinc flame spraying and painting, then assembled onto the car.
  39. 39. The anti-roll bar links had to be replaced with shorter items to shift the ends of the bar just above the outer CV joints. With the rear suspension all fitted the driveshaft clearance was checked with 2 people sitting on the back seat, the resulting 40mm clearance may just be enough allowing for bumps and the usual poor road surface. The rear suspension strut bump stops were later extended by approx 25mm with sections of the bump stops from the Jaguar subframe.
  40. 40. This was done after it was found that the driveshafts did contact the subframe when driving over potholes (every couple of feet) so the ride height will need to be addressed. The original Mondeo ST220 rear wheel sensors were integral to the rear hub assemblies so the Jaguar sensors had to be used instead. Disassembly of one of the Mondeo rear hub assemblies revealed that both the Mondeo and Jaguar wheel sensor tone rings although of different construction, have 32 interruptions (pulses) per revolution, so the ABS/ESP should function OK – thankfully it does.
  41. 41. The exhaust system The standard exhaust system consisted of front and rear bank exhaust manifolds each feeding straight into its own catalytic converter. The cats both exited into 2” diameter pipes which ran rearwards to the bulkhead where they fed through 2 flexi joints and into the first box, 2 pipes in and 2 out. Both pipes then fed into the next box, again 2 pipes in and 2 out. Leaving the second box both pipes joined from 2 x 2” into a single 2.5” pipe, which ran around the fuel tank then split once more into 2 x 2” pipes and then into each rear muffler. The Miltek exhaust system that had already been fitted took the output from both flexi joints into a single 2.5” pipe all the way back with no centre boxes before splitting into 2 x 2” pipes then into the straight-through rear mufflers. The catalytic converters needed to be removed with provision for fitting a single cat back in for the MOT and enlarging at least the forward section of the exhaust system to increase flow where possible. Due to the proposed future fitting of 4 wheel drive a single pipe had to be used from the front to rear to make way for the propshaft. The result is 2 x 2.5” down pipes from the manifolds both joining into a single 3.0” pipe at the bulkhead. Note the incorporation of a flexi section and sleeve coupling in the forward down pipe to aid fitting and accommodate some expansion related movement. A large flexi is also fitted after the y-connection to accommodate engine movement (torque reaction) as per the original system design requirements for a transverse engine. An M18x1.5 boss was also fitted after the y-connection for a wideband lambda probe.
  42. 42. After the main flexi-joint there is a 14” long removable section with V-band flanges for easy removal. This is where a cat can be swapped in for MOT. This work was taking place at the same time as additional work for the 4x4 conversion so the mid-rear section of the exhaust system was modified to run through the transmission tunnel in the fuel tank and around the rear differential. The rear section including mufflers was reused in modified form from the aftermarket Miltek system.
  43. 43. Looking rearwards from under the engine, the route of the exhaust system as well as the space for the propshaft can be seen. At this stage the gearbox, transfer box and propshaft cannot be fitted to complete the 4x4 conversion due to the fact that Performance 3000 only have a 2 wheel drive rolling road dynomometer and the ECU requires further calibration/mapping work. When the gearbox is changed it is proposed to take the opportunity to replace the clutch with a higher torque capacity item. There have been some reliability issues reported concerning the Jaguar transfer box which is assumed to be down to the use of lifetime oil and only 0.6 litres at that. It is proposed to fit an oil circulation pump and cooler to the gearbox and transfer box, probably using the main gearbox casing as the reservoir. Having previously purchased a transfer box as spares or repair, they do appear to be fairly solid except for the centre differential viscous coupling, which in this case was cooked. The apparent lack of oil was also noted, instead just greasy scum inside the casing.
  44. 44. Current state of engine bay: October 2009
  45. 45. Next: • Fit forged pistons and rods when they arrive, including new head gaskets, bolts and big end bearing shells (bearing source: Modus Engineering). • Fit shorter supercharger drive belt and correctly tension. • Develop fuel level sender interface/correction unit. • Attempt live datalogging with XCAL 3, and wideband O2 and MAP sensors connected to analogue inputs. • Sort out the handling – crap new tyres? Already tried 4 wheel alignment, removing the rear diff and refitting the original rear hubs and fitting old part worn tyres to rear. All made noticeable improvements but high-speed (squirming) instability still exists.
  46. 46. Update November 2009 Flow testing of standard Visteon ST220 fuel pump indicates that it will not meet the peak demand of the main pump so cannot be used in place of the Walbro unit. Instead the Visteon pump is fitted as the transfer pump – at least one pump is quiet. Have also had to make a small interface unit to allow the fuel gauge to operate using the two tank sender units. This includes a comparator circuit that shuts of the transfer pump when the fuel level drops too low on that side of the tank. Lift pump assembly with siphon valve removed Transfer pump assembly using standard ST220 fuel pump
  47. 47. Fuel pump controller – under rear seat Relays for in-tank fuel pumps
  48. 48. Note to self – tidy this up and make an access cover
  49. 49. Update Early December 2009 Forged pistons and rods arrived and workshop space organised to carry out work. All necessary gaskets, bolts, studs etc. sourced from Ford.
  50. 50. Disassembly – this is what a stripped ST220 Duratec 30 looks like
  51. 51. Original pistons and rods as removed New pistons and rods almost ready for fitting – the ring gap has to be checked by placing the rings in to bores prior to fitting to pistons. Undersize ring gaps enlarged with a ring grinder (or an oil stone)
  52. 52. Then things started to go less well… These are the big end shells of #6, no evidence of wear and look pretty good These are the big end shells of #1 showing heavy scoring due to some form of abrasive contamination in the oil. All except #6 are affected, although #1 is the worst. No sign of debris in oil so likely occurred before last oil change, however this could not be ignored.
  53. 53. The oil is drawn from the sump, through the pick-up and strainer, which appeared to be clean and into the oil pump. The oil pump was removed and disassembled for inspection revealing significant scoring of the rotors and housing – probably still fit for use but not happy so not going to take the risk. The oil pump then pumps the oil through the oil filter which evidently failed to do its’ job, and into the main oil gallery. Incidentally, have only ever used new, genuine Ford oil filters and good quality fully synthetic oil, very frustrating! The oil then passes from the main gallery up into the cylinder heads to lubricate the camshafts and supply oil to the hydraulic adjusters (and also from here to the supercharger). Thankfully no evidence of damage or contamination was found in the heads or supercharger, if so the project would have ceased here due to the cost of repair. The oil also passes from the main gallery to the crankshaft main bearings and through drillings in the crankshaft to the big end bearings where the damage was first noticed. This means that the contamination first had to pass through the mains before reaching the big ends. This presents a dilemma as Ford will only supply a complete short engine, no parts for the bottom end are available. Some internet research and a few phone calls later a few options were presented. Managed to find a new Ford Maverick 3.0 V6 oil pump on Ebay (same basic engine). The main bearing shells are available through engine builders (had already had to purchase big-end shells for the piston and rod upgrade, Federal Mogul part number – 7262M (standard size). The crankshaft oil seals are available through Ford under part numbers: F5AZ-6700, F5AZ-6701 (these are Ford USA part numbers). The main bearing cap bolts are torque-to-yield and will also need to be replaced, available from Jaguar (3.0 V6 X-Type, S-Type), part numbers: XR83302 (8 off), XR85191 (4 off), XR85193 (5 off), possibly also available from Mazda. Alternatively ARP now supply a main stud kit for the Duratec 25 and 30 engines under part number: 253-5402. Decided to dive in and remove the remainder of the engine from the car and strip the crank out. Turns out this may have been a good move as although the main shells were in reasonable condition, one had very deep scoring present. Luckily the crank seemed more or less ok so simply polished the journals with crocus paper and left it at that. The necessary parts were sourced and proceeded with the rebuild although having just added around £400 extra to the parts cost, really feeling the pinch now… Incidentally the piston pins are not an interference fit in the pistons as indicated by the information I’d read and are simply retained by round wire clips as per the aftermarket pistons – or at least that’s the case with my engine. It is therefore feasible to easily replace the rods only and reuse the standard pistons and rings.
  54. 54. The disassembled block and heads were flushed out and steam cleaned before rebuilding – didn’t want any more contamination.
  55. 55. Rebuilt bottom end with new bearings, pistons, rods and crank seals The new oil pump
  56. 56. Update 14 December 2009 Rebuilt short engine back in car – not easy, took 3 guys including myself to make that happen, albeit without an engine crane and just using a ratchet strap. Got it out on my own though… Engine more or less reassembled but still awaiting ARP main stud kit. I did call Jaguar before ordering the ARP kit as the standard parts are a lot cheaper (£41 vs £200) but unfortunately 1 of the part numbers is not currently available and the dealer was unable to advise lead-time. Engine currently built using original main bolts but not yet torqued up so cannot proceed any further and run engine up. Advised I could be waiting until the new year for the stud kit to arrive, not happy! Thinking ahead – Exhaust The new, enlarged, low back-pressure exhaust system sounds crap, awful rasp under load. Very McDonalds car park on a Saturday night, a chavs’ wet dream… Think removal of catalytic converters coupled with the long straight central section may have induced resonance caused by exhaust pulses being reflected up and down the mid-section. Have found a high flow cat with specified gas flow rate capability in the region of what’s required so will give that a try and see if it’ll work as a permanent solution to emissions and noise. If that fails to sort the noise then will try fitting a slim centre box under the fuel tank. Handling / suspension Not really made any progress with finding out what is wrong with the rear suspension so next step is to replace the rear sub-frame bushes with poly bushes and replace all the lower arms (tie rods already replaced), then have the a proper 4 wheel jig alignment undertaken.
  57. 57. Update 19 December 2009 The project has recently taken a slight backward step. Engine fitted with Wiseco forged pistons custom manufactured for 10.0:1 CR and forged K1 connecting rods. Engine is mechanically unchanged in every other respect and is as it left the factory except now rebuilt with new rods, pistons, standard bearing shells and standard Ford gaskets. The engine block and heads are aluminium and the block has cast iron liners. The block and heads have not been skimmed or re-machined in any way and were simply cleaned prior to re-assembly. The engine was rotated by hand before re-fitting the cylinder heads and turned smoothly with no problems evident. The engine was again rotated by hand after fitting the cylinder heads and all bolts correctly torqued according to the procedure stated by Ford, and some ‘tightness’ was felt as the pistons pass through TCD. At this point the camshafts were not fitted and all valves were fully closed so piston to valve interference can be ruled out. Alarmed and not having carried out a full engine rebuild on a large engine before I had a couple of other reasonably knowledgeable people ‘have a go’ who suggested this ‘tightness’ was just where the pistons were reversing direction through TDC and BDC. I proceeded to fit the camshafts, chains, tensioners, covers etc and everything seemed fine but the ‘tightness’ still worried me. I looked through some of the pictures taken during rebuilding the engine and wondered if the pistons were touching the heads through insufficient clearance. The new forged Wiseco pistons do have very large valve cut-outs to allow extra clearance for high-performance racing camshafts which this engine does not have – only the standard ST220 high-lift camshafts. To maintain the relatively high static compression ratio, the piston manufacturer has enlarged the dome of the piston and extended it closer to the edge of the crown – could this be hitting the heads? The doubt would not go away so the front head was removed to find evidence of the pistons interfering with the head at the edge of the combustion chamber – see following pictures. The piston supplier has been advised of the error and I’m currently awaiting action. After some thought, decided that I really do not want to remove and return the pistons due to the work and time involved. Examination of the areas of the pistons and heads that are interfering suggests that only a very small amount of material would need to be removed from the heads to remedy the situation, hopefully without significantly reducing the compression. Will pursue piston supplier to cover cost of replacement head gaskets and bolts (about £130).
  58. 58. Close view of installed piston View of combustion chamber
  59. 59. Outline of gasket / cylinder bore Marks where edge of piston dome has contacted edge of combustion chamber Mark on piston dome from contacting head
  60. 60. Update 26 December 2009 Both cylinder heads were removed and the required material carefully and evenly ground away and polished with a die grinder. This turned out to be a relatively easy job due to the availability of the proper tools, a rare occurrence. The heads were then dummy fitted without gaskets to simulate worst-case clearance and the bolts hand tightened. The engine was turned by hand as before and no ‘tightness’ was felt so the mating surfaces were cleaned again and the heads re-fitted with new gaskets and bolts, then torqued down according to the Ford procedure. Probably should have checked the clearance with plasticine… The engine was then rotated by hand once more before fitting the camshafts. This time the engine was tight through TDC again, much worse than before and one cylinder in particular so tight it cold not easily be turned by hand. Really, seriously unhappy at this stage. So, removed the front head again and… The gaskets are incorrect, the fire-rings are too small causing the gasket to overhang the bores, must be gaskets for the 2.5 V6 not the 3.0 – how did I not notice this? Put is down to poor workshop lighting but was still feeling borderline incandescent by this stage. Looking at the part numbers on the old and new gaskets and the invoice revealed that Ford have messed up so will hopefully replace the parts free of charge. Easy fix but more time lost and may end up paying for this as did not notice the error until after the parts were fitted. Modified front cylinder head
  61. 61. Before material removal After material removal
  62. 62. Obviously there are some concerns regarding modification of the combustion chambers in the cylinder heads to accommodate an error by the piston manufacturer: • How much is the static compression ratio going to be reduced by removing material from the heads? • How much has the piston manufacturer screwed up – has the compression ratio for these pistons been calculated correctly? • How much and in what manner is the swirl of the incoming charge and the flame pattern going to be affected by modifying the cylinder heads (not an easy one to answer for a diy-er)? Comparing the standard pistons to the forged pistons shows that although the standard items have relatively flat crowns, the forged pistons have enlarged domes to make up for the deeper valve clearance cut-outs. Both types of piston are ‘just’ sub-flush with the block deck at TDC. Some basic calculations suggest that a fairly significant change in combustion chamber volume would be required to greatly alter the compression ratio: Engine: 3000cc (approx), 6 cylinders Total swept volume = 3000cc Compression ratio = 10.0:1 Cylinder swept volume (uncompressed volume at BDC) = 3000 / 6 = 500cc Cylinder compressed volume at TDC = 500 / 10 = 50cc Removal of 1cc of material from the combustion chamber will result in a cylinder swept volume of 501cc and a compressed volume of 51cc this nets a compression ratio of: 501 / 51 = 9.82:1 1cc is quite a lot of material removal, a more likely increase of 0.5cc gives: 500.5 / 50.5 = 9.91:1 The guess here is that the piston manufacturer has machined the top of the domes to a diameter larger than they should have. Assuming all other dimensions are correct, this will of course increase the compression slightly, but that in turn will be offset by the material removed from the edges of the combustion chambers in the heads. The amount (volume) of material that needs to be removed to gain the required clearance is pretty minimal due to the very small area of piston to head interference. With the alternative being to press the currently unforthcoming supplier (to be fair this is the Christmas period) for replacement/re-machined (correct) pistons entailing a fair amount of work – bottom end disassembly, uninstalling and reinstalling all the rings, new big end bolts etc. and the huge associated delay, it was decided to go ahead with the cylinder head modification based on the assumptions mentioned above. There’s a saying about the nature of assumptions though, I just hope my impatience doesn’t prove it to be correct here…
  63. 63. Update 03 January 2010 Engine now fully reassembled with the exception of the sump and front down pipe. Chased supplier and have been advised that ARP main stud kit should arrive during the first week of this month. It transpires that the head gaskets for the ST220 engine are different to those used in that standard 3.0 V6 and Ford had ordered the wrong ones, they replaced the gaskets and bolts free of charge. Took the opportunity during reassembling the engine to fit a new larger air filter, which had been purchased some months earlier. The new filter is supposed to have a higher flow capability than the K&N item it replaces. During the last mapping session it was noticed (by temporary removal) that the filter was causing a significant airflow restriction. 89mm (3.5”) Also took the opportunity to re-route the supercharger oil feed line. The oil was originally taken from the rear cylinder head through an inline filter – there are ¼ NPT blanking plugs in the oil passages that run up the transmission end of the head to feed the camshafts and hydraulic adjusters. Was never particularly keen on this idea as the oil feed from the block into the head is not very large. During rebuilding the engine I noticed that there is a blanking plug adjacent to the oil pressure switch, unfortunately it is right behind the AC compressor with minimal clearance.
  64. 64. So it was decided to remove the oil pressure switch and take the oil from there. The pressure switch has been relocated into the supercharger oil feed line just after the inline filter. Spare blanking plug Original location of oil pressure switch Supercharger oil feed line
  65. 65. Update 28 February 2010 The ARP main stud kit never did materialise. After much chasing the supplier admitted they were having trouble with the importers and agreed that I could cancel the order for a full refund. So with the money back in the bank I called Jaguar who now had their equivalent parts available at a quarter the cost of the ARP parts. This however was not without problems… Turns out that the Ford and Jaguar engines have slightly different windage trays and oil pick-ups and consequently different mounting points. The windage tray is simply a baffle plate that sits under the main bearing caps/ladder to stop the crankshaft whipping up any oil that splashes up therefore reducing windage losses. The Ford tray is mounted by studs on the ends of some of the main bearing bolts as shown below, one of these studs also holds the oil pick-up support. There are a total of 17 main bolts, 8 of which have the additional mounting studs for the windage tray. The bolts nearest the crank are M10 and the bolts further out to each side are M8.
  66. 66. The Jaguar main bolts are shown below
  67. 67. The 2 top bolts are the M8 bolts and the one at the bottom is M10, note the absence of any studs on the M10 bolts. This caused some stress, after which the windage tray was slightly modified and 1 of the original ford bolts re-used where required to hold the oil pick-up support.
  68. 68. With the bottom end now fully reassembled and all main bolts torqued to specification, the sump and exhaust were refitted and the engine filled with all appropriate fluids. The engine was then cranked on the starter with the coil pack disconnected and the main fuel pump fuse removed to prime the oil system. Thought this would be fairly simple as the oil pump had been correctly primed during engine rebuild, then remembered that the engine had been turned over several times by hand to check nothing was wrong. It took ages for the oil pump to draw any oil let alone build pressure so ended up cranking with the oil filter partially loosened so that the pump only had to pump against a very short oil channel (and onto the floor). Eventually oil was flowing, the filter was tightened and almost immediately the oil pressure warning light extinguished. With everything reconnected and the ignition turned on and off a few times to run the fuel pumps and prime the fuel system, then engine was started. The oil warning light stayed out and all seemed to be running fine apart from a slight knocking noise. The engine was allowed to idle to get the coolant up to temperature and open the thermostat so that the coolant level could be correctly topped up, at the same time hoping the knocking noise was simply a hydraulic lifter that had not yet filled with oil. After about 15 minutes of running, the knocking noise did not improve, nor did it get any worse so performed the stethoscope trick at various points around the top and bottom of the engine. The noise sounded more like a bottom end knock of sorts but not easy to locate. At this point the engine was switched off and begun to wonder what this noise was. Later the oil was drained and the sump removed to see if the crank was touching the windage tray. It had been noted during rebuild that the Jaguar main bolts have thinner heads than the Ford items therefore moving the windage tray a millimetre or two closer to the crank. This would have been a simple fault and an easy fix but unfortunately this was not to be the case. The amount of clearance was not obvious or at all easy to measure so the tray was removed and inspected, no marks were found. The tray was then cleaned, spray painted on the crank side to highlight any contact points, refitted, engine turned over on the starter then removed and re-inspected. Again no marks were found. I then looked more closely at the remaining oil in the bottom of the sump, which had previously been cleaned during rebuild. There was evidence of fine metallic particles in the oil. Worried! All the main bearing and big end bolts were checked in case I’d missed any during tightening - I hadn’t. The crank was rocked by hand and the big end caps tapped with a small mallet in an attempt to detect any obvious looseness due to excessive clearance, no problems were detected.
  69. 69. Next was removal of the rocker covers to check all the lifters and roller rockers – no problems found here either. Both timing chains also checked and found to be correctly tensioned. Running out of ideas I called my local engine rebuild specialist for advice. Their suggestion on top of what had already been checked was to look at the bores to see if anything had picked up - aluminium from one or more of the pistons deposited on the surface of the bore(s), due to insufficient lubrication or running clearance. Was very difficult to see much of the bores looking up past the crank but did notice what looked like a streak of something on the thrust side of one of the bores. Feeling around the bores with an aluminium welding rod confirmed that there was something on one of the bores. This meant another total engine strip-down – déjà vu excess!!! The proceeding engine strip-down confirmed that one of the pistons had indeed picked up in the bore, but why? All the pistons were a pretty loose fit and being perhaps being a little naïve and not expecting serious problems, I’d omitted to actually measure the piston to bore clearance during rebuild. A quick check around all the pistons with a feeler gauge confirmed that they all had at least the 0.004” clearance recommended by the piston manufacturer so insufficient clearance was not an issue. The oil pressure warning light had gone out quickly during engine start-up and without a pressure gauge could only assume the oil pressure was good – there was no reason for it not to be. The (new) oil pump was checked over and no issues were found with either the pump rotors, housing or relief valve. Then it dawned, the cylinders are splash lubricated only by oil slung from the con- rods. The bottom end of the engine had sat in the car in a partially rebuilt state for several weeks and been turned over numerous times by hand to check out the clearance issues caused by the incorrectly machined pistons and then the incorrect head gaskets. The bores though well lubricated during rebuild were probably fairly well scraped free of oil by the time the engine was cranked for priming the oil system and then subsequently likely to have been started dry. Still don’t quite see why an aluminium piston would pick-up that readily on a cast iron lined bore though. After some discussion on the phone the engine block complete with crank was removed and taken along with the forged pistons and the original Ford pistons to a local engine rebuild specialist for inspection. They measured the bores and both sets of pistons and advised that the clearance with the standard pistons (cast, hypereutectic with low-friction coated skirts) was around 0.003” – three times what the Ford specifications state. The piston to bore clearance with the forged pistons was 0.004” to 0.0045”, within what the piston manufacturer advises. Left the block with them to have the bores honed and the crank for a light polish. New bearing shells and bolts will be used upon rebuild. Also contacted the piston supplier and advised I’d like to take up the manufacturer’s offer of replacement pistons due to the original machining error. Was quoted at least 4 weeks delivery.
  70. 70. With everything now set in motion for another engine rebuild it was decided to spend the interim sorting some other issues that need attention. Flywheel Previously during engine rebuild it had been noticed that the standard ST220 flywheel is indeed a dual mass flywheel and some backlash was evident in the damping mechanism – could this have been causing a knocking noise? The clutch was starting to feel a little ‘juddery’ on take-up before the engine work began so maybe the flywheel backlash was the cause. Indeed the clutch itself is only 30,000 miles old as the original was replaced under warranty and is showing very little signs of wear. After many evenings spent searching the internet for a suitable solid DMF replacement flywheel to no avail, I was lent an ST200 solid flywheel to try out and sourced a suitable used clutch through Ebay. Unfortunately after a few measurements it was found that the ST200 flywheel is too short and does not sit far enough onto the gearbox input shaft spline. It would work, but probably not for long. The input shaft is obviously a different length for versions used with a normal solid flywheel and those used with a DMF. Back on the internet for some more searching and a company called TTV Racing were found who manufacture various machined automotive components including lightened and DMF replacement flywheels for various proper cars including the ST220. A few emails, a quote and a phone call later, one was ordered up. ST220 OEM dual mass flywheel and clutch assembly:
  71. 71. TTV Racing single piece solid steel flywheel
  72. 72. Was surprised at how light the new flywheel is as its not even one of the ‘Super-Lite’ flywheels manufactured by TTV racing. Also slightly concerned, if the engine now idles rough with this much lighter flywheel, the supercharger’s gearbox will make a rather irritating chattering noise as it already does if the engine ‘hunts’ during idling. On the plus side the engine will be a lot more responsive, whether that’s good or bad is yet to be seen, thinking possible further supercharger belt slip issues… Just for reference purposes I decided to weigh the old and new flywheels with the following results: OEM ST220 DMF (excluding clutch assembly) = 11.1Kg TTV Racing solid lightened ST220 flywheel = 4.1Kg Original Ford clutch assembly including pressure plate = 5.9Kg OEM ST220 DFM + standard clutch and pressure plate = 17.0Kg TTV Racing flywheel + standard clutch and pressure plate = 10.0Kg
  73. 73. Rear suspension Ever since the rear sub-frame was modified to accept the rear axle components of the 4-wheel drive system there was some observed vagueness of the rear end, which was never fully resolved. Virtually everything had already been checked over or substituted in an attempt to eliminate the cause of the problem: hubs/bearing carriers, sub-frame alignment and geometry, brakes, tyres etc. All showed an improvement but did not fix the problem. Next step is to replace all the rear suspension bushes, all appear ok but for the cost might as well replace. So, a set of Powerflex rear sub-frame bushes were fitted along with 4 new lateral arms. The tie rod arms and anti-roll bar bushes and links had already been replaced. Unfortunately the original sub-frame bushes were in very good condition and had to be burnt out with an Oxy-Acetylene torch thus also requiring the sub-frame to be blasted, Zinc sprayed and painted again. The polyurethane Powerflex bushes were pressed into the sub-frame after being well coated with polyurethane adhesive / sealant – don’t want anything moving!
  74. 74. Compression ratio With the engine once again disassembled and the cylinder heads removed it made sense to measure the combustion chamber volume of the modified heads and calculate the effect on the static compression ratio. The conventional method involves placing the cylinder head upside-down and level with valves and spark plugs fitted. With a little grease an acrylic or glass plate is sealed over the chamber to be measured. The chamber is then filled with oil from a burette through a small hole in the middle of the plate. The volume of oil admitted through the hole from the burette is measured and when the chamber is completely full and free of bubbles this corresponds to the chamber volume. There’s one problem with this: an accurate burette is required that will measure liquid volume down to around 1/10 cc or so depending on how accurate you want to be and I didn’t have one. There is another way though – measure the liquid volume by mass (I did have some reasonably accurate scales). Tap water weighs near enough the same as pure water at 1.00grams/ml, 1ml = 1cc. A small beaker of water was weighed, the combustion chamber was then filled with water from the beaker with a pipette until full with the meniscus just rising into the hole in the Acrylic plate. The beaker was then re-weighed, the difference being the mass of water used in grams and hence the combustion chamber volume in cc. Very simple but a little fiddly.
  75. 75. This yielded the following results: Cylinder Total Remain Volume 1 88.94 40.92 48.02 2 125.60 77.29 48.31 3 104.30 55.67 48.63 4 99.07 50.53 48.54 5 92.52 43.76 48.76 6 94.69 45.90 48.79 The chamber volumes span 48.0cc to 48.8cc, which seems relatively large variation but then any small bubbles trapped in the spark plugs or around the valves that may have gone unnoticed could throw the volumes out slightly. The relevant specifications for the standard ST220 engine are: Displacement: 2967cc Bore: 89.0mm Stroke: 79.5mm Chamber volume: 48.2cc Head gasket thickness: 1.0mm Deck clearance: 0.415mm below to 0.115mm above (assume -0.10mm) The deck clearance is the distance between the top of the piston crown and the deck of the block. Most of the piston to head clearance around the bore circumference is due to the thickness of the head gasket. The compression ratio is calculated as the ratio of the total cylinder volume at BDC (max) divided by the volume at TDC (min). This is due to the variable swept volume of the piston in the cylinder, and the additional fixed volumes due to the deck clearance, head gasket thickness and combustion chamber. This does assume that the pistons have flat crowns as the shape of the crown will also have a significant effect – this can be calculated. Incidentally the standard pistons do have very flat crowns with very small valve clearance cut-outs and a small, very shallow dome presumably to compensate. The forged pistons have much deeper valve cut-outs to allow for higher lift camshafts and consequently much taller domes to compensate. Cylinder swept volume = ((π x bore2)/4) x stroke = ((π x 8.902)/4) x 7.95 = 494.58cc Volume due to gasket = ((π x bore2)/4) x thickness = ((π x 8.902)/4) x 0.10 = 6.22cc Volume due to deck clearance = ((π x bore2)/4) x clearance = ((π x 8.902)/4) x 0.01 = 0.62cc
  76. 76. Compression ratio with specified combustion chamber volume of 48.2cc = Cylinder vol. + gasket vol. + clearance vol. + chamber vol. / gasket vol. + clearance vol. + chamber vol. = (494.58 + 6.22 + 0.62 + 48.2) / (6.22 + 0.62 + 48.2) = 549.62 / 55.04 = 9.99 Compression ratio with minimum measured chamber volume of 48.0cc = (494.58 + 6.22 + 0.62 + 48.0) / (6.22 + 0.62 + 48.0) = 549.42 / 54.84 = 10.02 Compression ratio with maximum measured chamber volume of 48.8cc = (494.58 + 6.22 + 0.62 + 48.8) / (6.22 + 0.62 + 48.8) = 550.22 / 55.64 = 9.89 So the actual compression ratio should be between 9.89:1 and 10.02:1 Due to the significant effect the deck clearance has on the cylinder volume and compression ratio, this will need to be measured during rebuild for an accurate compression ratio calculation. Not sure quite why my measured combustion chamber volume varies both above and below specification. Can only assume this is due to measurement errors on my part. Would guess that the higher measured volume is probably the more accurate as I was pretty careful not to lose any water so its more likely the low reading was due to trapped air that went unnoticed.
  77. 77. Exhaust Also took the opportunity to correct part of the exhaust system that had originally been rushed due to the unavailability of a suitable part at the time – where the mid section reduces from 3.0” to 2.5” just in front of the rear axle.

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