Showing posts with label modification. Show all posts
Showing posts with label modification. Show all posts

01 June, 2010

Vapour Lock

Owners of the 1999 and 2000 model of the Suzuki Hayabusa may face this problem when they were to increase the engine compression (in one way or another); resulting in higher ambient temperature under the fuel tank. Add to that equation a in line fuel filter, it's a very good recipe for vapour locking the fuel system.

According to wikipedia,

Vapor lock (also known as vapour lock) is a problem that mostly affects gasoline-fueled internal combustion engines. It occurs when the liquid fuel changes state from liquid to gas while still in the fuel delivery system. This disrupts the operation of the fuel pump, causing loss of feed pressure to the carburetor or fuel injection system, resulting in transient loss of power or complete stalling. Restarting the engine from this state may be difficult. The fuel can vaporise due to being heated by the engine, by the local climate or due to a lower boiling point at high altitude.

The 99-00 model of the Suzuki Hayabusa utilises the external fuel pump as opposed to the in-tank fuel pump from 01 model onwards. This provides the opportunity for vapor lock to occur. The external fuel pump runs 2 fuel lines, 1 inlet and 1 return line. The inlet is gravity fed and is not pressurized. This allows the fuel to vapourize when the engine compartment temperature rises too much due to heat soak.

The fuel pump when moved to the interior of the tank helps prevent vapor lock, since the entire fuel delivery system is under high pressure and the fuel pump runs cooler than if it is located in the engine compartment. Under high pressure the fuel will be harder to vapourize and thus vapour lock is almost unheard of in K1 models and above.

What are the causes of vapour lock?

A vapor lock is more likely to develop when the vehicle is in traffic because the under-hood temperature tends to rise. A vapor lock can also develop when the engine is stopped while hot and the vehicle is parked for a short period. The fuel in the line near the engine does not move and can thus heat up sufficiently to form a vapor lock. The problem is more likely in hot weather or high altitude in either case.

What are some solutions if you have a vapour lock issue?

  1. Rerouting of the fuel lines away from heat generating components,
  2. installation of a fuel cooler or cool can,
  3. shielding of heat generating components near fuel lines,
  4. and insulation of fuel lines.
Amongst the above suggested solutions, you can also consider swapping to an in-tank fuel pump which requires the replacement of the entire fuel tank, fuel pump some fuel line fittings. I have personally tried items 3 and 4 with good results.

If you have a fuel problem, do check if it is caused by vapour lock. You would want to be caught stuck in traffic with a stalled engine and unable to start due to the vapour lock issue.

02 January, 2010

Exhaust Performance and Scavenging

A very clear and concise explanation of the process of exhaust gas scavenging and how it's affected by exhaust size, length and cam timing.

The Basics

As are most things automotive, the exhaust system is a compromise. It must balance noise and performance. In addition, the exhaust system can be designed to increase performance in the low RPM range or at the top end. All of these aspects must be taken into account when designing the best possible setup for a given application. A larger pipe diameter typically will reduce backpressure allowing the engine to expend less energy pushing out exaust gas. If the system was being restricted, this will result in more power at a certain range of RPMs. The downside to larger pipes is a loss of power in other areas of the power band and increased noise.

Scavenging

At first glance one might think that a maximum pipe size would result in the best performance. It should provide the most flow. This is true for a steady stream of gas. An engine ejects exhaust gas out of the ports in pulses though. This results in a stop-go-stop-go situation as the exhaust valve opens and closes. A properly sized pipe will help to suck the gases out of the cylinder at certain RPMs. Since air has mass and velocity, it has momentum. When in the scavenging RPM, the exhaust charge exiting actually creates a vaccum for part of the exhaust stroke. This provides for a nice boost in power and torque. For ideal scavenging an exhaust speed of 240-260 feet per second is desired. Thus as engine speed increases for a given displacement so must the pipe diameter.

Below is a typical graph of exhaust port pressure vs. piston position:


NOTE: The exhaust pressure during scavenging nets out to be positive. Thus there is not an all around vaccum. Energy is still being wasted pushing exhaust gas out. The scavenging is not "free". Work is still done. Scavenging merely helps to aliviate what would be even more work being done by the engine. Also note that the psi values will vary from engine to engine, but the curve remains approximately the same. Values over 6 psi are generally considered excessive backpressure.

The graph above is a typical representation of what exhaust port pressure looks like as the engine rotates through almost a full revolution during the scavenging RPMs. Exhaust pressure builds as soon as the exhaust valve opens. This occurs before bottom dead center. Most of the torque the engine generates is produced by 90 degrees, thus it is not necessary to keep the exhaust valve closed much past 90. By opening the exhaust valve early, the high cylinder pressure helps to accelerate the charge in the exhaust manifolds. Pressure peaks before bottom dead center and then rapidly falls as the accelerated charge pulls the exhaust out of the engine. As the piston approaches top dead center, the intake valve opens. Pressure drops again and the exhaust gas actually helps to suck the intake charge into the cylinders.

These ideal conditions can only be met at certain RPMs. To do this one can vary the size of their piping to chose what will provide them the best performance. Smaller pipes will move an equal volume of gas at a higher speed. This typically comes at the expense of increased backpressure (resistance to flow) which inturn leads to poorer performance. A smaller pipe will help to maintain the ideal exhaust gas velocity when the engine is running in the lower RPMs. This provides for a torque boost off the line with improved streetability and driveability. For this reason many manufacturers size their pipes on the more conservative side. As the RPMs increase though, the backpressure builds due to the excessively small pipe size. This pushes the velocity of the exhaust gas out of the scavenging range and saps power on the top end, reducing performance in that spectrum.

A larger pipe will maintain ideal exhaust gas velocity on the top end. This will increase peak power. The downside comes with a slow exhaust charge on the low end. Their will not be enough suction to aid in the expulsion of exhaust gas. Torque will suffer in the low ranges for this reason. Too large or too small of a pipe will push the scavenging bonuses out of the useable RPM range and will result in diminished overall performance. It is important to size the piping correctly for the desired application: low end or top end. One should also consider how this will effect the rest of the car. For instance, if the car has an automatic with a stall speed of 1,500 RPMs it won't do any good to have all the power on the top end when off the line performance will suffer terribly. Likewise if the car is mainly driven in the city or through heavy traffic, a lack of low end grunt might make driving more of a chore.

On valve overlap scavenging also helps to draw in the fresh intake charge. The pressure in the exhaust port drops again and the exhaust flows more easily. It should be noted though that too much exhaust velocity on overlap can cause "over scavenging". This occurs when the exhaust vaccum becomes so great, due to overly small tubing, that it actually sucks the intake charge right through. This leaves spent charge in the cylinders and causes a loss in performance.

Common Views

A couple of commonly recommended modifications are increasing backpressure for lowend performance, and the use of equal length headers. Backpressure is almost always a bad thing. The higher velocity of a smaller pipe is what one wants on the low end. Unfortunately this ultimately chokes off the top end to an extent. Since these two go hand in hand (small pipes and top end back pressure), people often consider them the same. They are not. Putting a sharp bend in a pipe will cause high backpressure, but it will have little benefit for performance and scavenging. Backpressure is very useful for quieting an exhaust though and muffling the sound waves. As for equal length headers, companies often claim that they help with scavenging. They are used to line the exhaust pulses up. This can help during scavenging as the exiting charges will not try to occupy the same collector at the same time. Instead, the exhaust pulses will alternate and "zipper" there way into the collector. This results in smooth flow and optimal performance. Equal length headers, or headers designed to take advantage of scavenging in general are a plus. It is important to buy from a reputable company though as equal lengths will not guarentee optimal performance. Dynometer testing is the best way. Most reputable exhaust companies do make use of a dyno which gives some assurance as to what one is getting.

Summation

1. Choose a smaller pipe for better low RPM performance, a larger one for high RPM performance.

2. Remeber that peaks are not everything, as seen in Understanding Performance, thus a proper sized pipe will deliver better results than one that may give the highest peak low end or top end performance.

3. Back pressure is almost always a bad thing.

Article from: http://autolounge.net/tech/exhaust.html

26 September, 2009

Westfield vs Zonda

Another one of the track oriented car running the GSX1300R Hayabusa engine. This one is so well designed that it beats the Pagani Zonda round Top Gear's test track.

03 September, 2009

8 Litre V10 Bike

When people think of large capacity engine bikes, a 8.0litre V10 engine will not like cross their mind. Here's one that's pushing out 500bhp with the engine taken off a Dodge Viper. Think this looks a lot more sensible than the Tomahawk.

22 July, 2009

24volt Start System Harness With Dual Battery Auto Charge Circuit


Designed for those who need a 24 start system and don't know how to wire it up. Tiger Racing has just what you need. This custom 24 start harness has everything you need to hook up a second battery with all plug and play connectors. Both batteries will auto charge with bike is running. No switches to mess with.
If you have a big bore motor, you'll want one of these for sure.

Price: $159.95 USD

As I saw this product on sale, it actually amazes me the profit margin of such products. As mentioned in the earlier post, it's actually a rather simple circuit, and the cost of the components are not too high as well. Anyway, the same can be said for this circuit. I've already gotten the circuit diagram out for ages, just never gotten down to wire it up for my bike. I'll be staying with my manual switch for a long time to come I guess. Until the day my hand itches for some DIY project, this will be next in the list.

27 June, 2009

Top Clamp Cover Makeover

Have been looking at the top clamp cover, it's all worn and old... And so comes the idea of having it made over...

Before - Top clamp cover with the metal emblem that says "Hayabusa"


After - Matt black with a metallic Suzuki logo (blocked by my VR2)



Ignition Key cover (which actually is the immobiliser antenna for the GEN2 Hayabusa)

With that fitted, it just adds to the list of useless but nice looking items fitted on the bike. Took about 20mins to remove the old and install the new. Since it's stock (from the GEN2 Hayabusa), once mounted everything simply falls back in place. No drama at all.

22 May, 2009

Wiring Schematic for 24V Start with Manual Switching

As promised, the following is the wiring schematic for the 24V starting with manual switching as mentioned in the post here.


This is a crucial electrical wiring to the bike and carries high ampere current during cranking. I will not be held responsible if any problems resulting in injuries or damage to the bike occurs. Please do this at your own risk.

19 May, 2009

Beyond Superbikes: The Yoshimura Hayabusa Fujio Yoshimura talks about the Japanese built GSX-1300R Racer

196 horsepower, 408 pounds, 200mph
"Racing Superbikes is okay, but there is no excitement," deadpanned Fujio Yoshimura as he began his explanation of why the roadracing planet's best known tuning firm is not competing in the Japanese All Japan Superbike championship in 1999.

"The (Suzuki) factory does their own thing, and there's no chance for a (satellite team). I decided to let (the factory) do the all-out war, and we'll do the X Formula class. I think that's more fun."

The Japanese X Formula class bears some resemblance to the AMA's Formula Extreme in that both classes are aimed at the bigger displacement bikes such as the Honda CBR900RR and the Yamaha R-1. There are three significant differences in Japan, and they are that the factories are barred from having in-house racing teams in X Formula, X Formula bikes can be claimed for 2,500,000 yen (~$20,000), and the X Formula bikes compete with the Superbikes on the track. These three significant differences combine to level the playing field between the factory teams and the privateers.

Well, level is a generous statement, as the factory supported superbikes still out-qualify and out-run the X Formula bikes. At least the difference in lap times between the shiny teams and the duct tape teams doesn't approach three to five seconds, as is starting to happen in AMA Superbike races.

"The factory system is so precise now, so efficient," the son of legendary Pops Yoshimura lamented. "Everything must be tested and done well. For a privateer team like us, we just don't have the resources." Yoshimura's claim of being a privateer team lacking in resources defies what is seen at the race track in America, but the purposes of Yoshimura USA and Yoshimura Japan are much different.

The factory wants to do their own development and things, you know," continued Yoshimura. "The U.S. side of Suzuki, they don't have any factory to do such an operation, so we're doing it for them. They have their own team for motocross, but they don't have anything for roadracing. (Suzuki U.S.) have their own team for motocross, but they don't have anything for roadracing. (The U.S. factory bikes) come directly from Suzuki-Japan to U.S. Yoshimura. I own the company, but I let the guys in California do the business."

Hence in Japan Yoshimura is completely on his own for turning the Hayabusa from a street bike to a race bike.

As for the modifications to the Hayabusa, the answer was classic Yoshimura:
"You can't do anything."

Uhhh .... Nothing? Fujio, come on.

Yoshimura then admitted to his Hayabusa having special pistons.

And a special camshaft.

And specially made close ratio gearbox.

And the Superbike kit GSX-R750 fuel injection system, with higher pressure and in-tank pump.

And the GSX-R750 Superbike kit swingarm.


"We're researching this bike for the people in America, Europe, and also in Japan. I know they love those things," Yoshimura explained. "These special parts will be available in another two months. I'm sure the people in the States will want a lot of tuning parts."

"Right now we're putting out about 196 hp. We began at 165. So we added another 30 hp without spending too much money, just changing the camshaft and the pistons."

Besides the swingarm change, Yoshimura has worked hard at reducing the weight of the Hayabusa. "It's down to 185 kg (408 lb.) now, about 100 lb. lighter. But it's still 50 lb. heavier than a Superbike. It's quite a handicap."

Even with the extra weight, the Yoshimura Hayabusa can accelerate to an impressive top speed figure. "I think we're the fastest on the track, 284 kph (176 mph). We're getting 10 kph on the Superbikes."

Suzuki race kit swingarm =$15,000Further weight reduction and further horsepower improvements can be realized, but at this stage in the Hayabusa development the concern has been transmission durability. "It comes down to the size of the motorcycle. The actual transmission gears are so heavy duty for the size of the bike. It will not shift as well as the racing one, because the gears are so heavy. I don't think there's so much we can do about that, we have to live with that. That's my concern though, how the transmission would hold up with that much horsepower and torque."

If Yoshimura had stayed with Superbikes, this kind the question of transmission capability would probably never come up. There lies the appeal of the X Formula class: the lack of technology creates opportunity for new technology more so than a situation where technology is plentiful.

"A lot of people ask me, 'Why you start racing the Hayabusa?'," Yoshimura admitted. "I keep telling them that I can't go back 25 years when the original Superbike racing started in the States with the Kawasaki Z-1. Those days are gone. Superbike is not like that anymore. The fans are a lot more enthusiastic about the out come of that bike (the Hayabusa) than Superbikes. With me, it's the same."

-- Images and text by Tracy Hagen. Copyright 1999, All Rights Reserved








SPECIFICATIONS POWER:142kw(193ps) / 10,000rpm
TORQUE:142.2Nm (14.5kgm) / 8,000rpm
WEIGHT:198kg (DRY) STD : 215kg
MOTORCYCLE GSX1300R 2000Model
ENGINE PARTS Tri-Oval Titanium Cyclone Exhaust System
Pipe : Titanium / Silencer : Carbon
φ81 High Compression PistonKit (12.0:1 Forged)
ST-1 Camshaft Set
TUNING UP
(ENGINE)
Cylinder Head Porting
Valve Polished & Lightened
Dyno Tested
Re-assemblled by YOSHIMURA FACTORY
BMC Air Filter
TUNING UP
(CHASSIS)
Original Oil Lock Piece,Piston Valve Shim & Oil Height
CHASSIS PARTS Aluminium Fuel Tank Capacity : 24Litter
Fairing Kit Upper,Lower, Carbon Front Fender, Seat, Screen, Tool Box, Seat Rail, Mirror, Head Light (High : Halogen / Low : HID),Turn Signal etc.
Fairing: Coloring YOSHIMURA Original Colour(Red & Gun Metal)
Magnesium Step Kit Adjustable Back: 19 or 31mm/UP: 49 or 61mm
Hydraulic Houses Front Brake, Rear Brake and Clutch Hoses
Digital Dual Temp Meter Set Water & Oil Temperatures,Voltage,time & Stopwatch
Chassis Protector
Brake Pad Set
OTHERS Racing Stand
Serial Number : Cylinder Head
Serial Number : Original Name Plate Yoshimura Hayabusa X-1 Book

24 April, 2009

1100cc 2-stroke triple Superbike

Imagine the power to weight ratio of what the Superbikes are getting these days. Imagine adding 50% more to that! Imagine no more as there's a bunch of crazy enough people to build a 1100cc 2-stroke engine making more than 250hp.


One for the "Because We Can" file: What do you do when you're bored with the paltry horsepower from a garden-variety Japanese superbike? We've seen power output from the Japanese fours plateau around the 150-hp mark (at the rear wheel on a dyno) for a few years now, and the OEMs seem to be focusing more on rideability rather than the exponential increases in torque and horsepower we've grown accustomed to over the last three decades. If they can make 220 hp MotoGP bikes, they can make them for us. If they wanted to.

Stephen Rothwell of The Two Stroke Shop, located in Tropical North Queensland, Australia, decided to tackle this crisis by using tried-and-true technology: the two-stroke engine. Rothwell had heard enough of legendary two-strokes like the Yamaha TZ750, so he decided to build his own legend. Rothwell and partner Wayne Wright (who designed two-stroke motors for GP race teams in New Zealand) were already building complete top-end kits for Yamaha two-stroke motors, so they already had some of the parts and the know-how for such a project.

"What the world needed was an answer to the current literbikes, which we find anemic," Rothwell told me over the phone. "If a bike can't hoist the wheel in 4th gear off the throttle it's not a superbike." The 1100cc three-cylinder TSS1100GP should have no such problems; when completed, it should make 250 hp at the rear wheel and 160 ft.-lbs. of torque. A powervalve will keep things rideable, with a characteristic hit of power as the revs climb. The chassis will be a lightly-modded Kawasaki ZX-10R ("it's beefy enough") and Rothwell expects the wet weight to be under 340 pounds: "when you dismantle a literbike and see how heavy that four-stroke motor is, it's just sad, really." The next project? The 112-hp TSS500 engine installed in a Yamaha WR450 supermoto chassis. "There's nothing 'super' about a four-stroke supermoto," sniffed Rothwell.

Not crazy enough? Rothwell and Wright can build you a 2200cc four-cylinder that could pump out 500 bhp and 300 ft.-lbs. of torque (add 10% if you want to run alcohol), although he admits that would be "far too much for a motorcycle, even by our standards." But the goal of TSS isn't to crank out demented one-off specials for wealthy lunatics. Rather, it's to bring attention to the efficient, powerful, and even environmentally friendly (Rothwell says these engines could be Euro3 and CARB compliant with the use of direct-injection technology) potential of two-stroke motors. The hope is that the Japanese factories will return to the smokey, wheelie-ing ways of their youth (minus the smoke) and build light, fast and durable motorcycles that can scare the crap out of us.





For more information: click here

23 April, 2009

New Map Loaded

Loaded a new map into the power commander just now. Made some adjustments based on all the rides I've been doing over the months.

Lean down some of the regions for fuel economy when going touring and chugging along in stop-and-go traffic. Also tried to keep a certain level of richness in that mixture to reduce the running temperature of the engine.

Overall throttle response have improved, toned down a bit of the torque at the lower end to help the engine rev up faster through the lower ranges. Pulling harder now with the faster revs. Shall do a separate dyno run to verify the results on the 2 maps.

Dyno will be posted at a later date when I get some time to go do the runs.

20 April, 2009

The Corbin Beetle Bags for GEN2 Hayabusa -in development -

Here are some of the pictures taken from the corbin website detailing the development process.










It's gonna look real sleek when it hits the market.

14 April, 2009

Williams Helical Camshaft

Introduction

The Williams Helical Cam (WHC) is a new type of mechanical Variable Valve Actuation system (VVA). More specifically it is a camshaft which allows the valve opening duration to be varied over an extremely wide continuous, stepless, range – all the added duration being at full valve lift.

The WHC was developed in the early years of the 21st century and of all the competing types of mechanical (that is, not “camless” types - electromagnetic or hydraulic) VVA systems it would appear to be the most capable and promising. It is still little-known amongst the mainstream automotive engineering community. One of the surprising and little-known facts about VVA systems in general is that, almost without exception, they are not new ideas. Most were first heard of many years ago – some have their origins in the age of steam engines. That they are not in wide use is a reflection that they are all lacking in some aspect of variable valve actuation.



For example, probably the most widespread in use and the most successful is the Honda VTEC (and the essentially very similar systems from other companies). There is no question that VTEC is very effective – in the Honda S2000 the engine power is virtually doubled compared to a non-VTEC version of the same engine. Otherwise its capabilities are limited. Its operation is strictly a stepped process and this precludes its use in the more exotic forms of engine load control.

Current research into these forms of load control includes Early Inlet Valve Closing (EIVC), Late Inlet Valve Closing (LIVC) and Homogenous Charge Compression Ignition (HCCI). None of the existing available mechanical VVA systems can adequately allow any of these forms of load control. BMW’s Valvetronic probably comes closest to being able to perform EIVC but even here it is not wholly successful. At valve opening durations short enough to allow idle and very low load situations, the unavoidable very low valve lift (that must accompany short duration with this type of system) has a throttling effect – and that is exactly what EIVC is trying to avoid. With the Valvetronic the effect is more “throttling-by-low-valve-lift” than true EIVC. It would seem almost physically impossible to achieve sufficient valve lift at durations short enough to allow true EIVC – maybe not even with electromagnetic/hydraulic VVA arrangements. The BMW Valvetronic is an example of the “oscillating cam” class of mechanical VVA systems – there are many, many other members of this class in the files of the US Patent Office, all with the same limitations.

Details

The WHC is distinctly different from competing VVA systems in that it incorporates a new and unique mechanical principle. Genuinely new mechanical principles are almost unheard of – especially in the automotive world. The WHC very distantly belongs to the very numerous general “coaxial-shaft-combined-profile” class of cams as most recently typified by the work from Clemson University (whose cams are essentially identical in principle to many other cams in the USPTO files, first appearing as early as the 1920s, number 1527456 from 1925 being a good example). This class of coaxial cam varies the valve opening duration by moving the relative positions of two adjacent cam lobes on the one coaxial camshaft in a circumferential manner – the follower riding on the combined profile of both lobes.

The inescapable problem is that the duration range is not very wide. Not enough for power at really high RPM and certainly not enough to attempt engine load control by LIVC. The WHC importantly differs from other members of the general class by having a unique helical movement – a combined circumferential and axial movement of the two profiles. Surprisingly, because of this movement, the WHC in theory has no practical upper limit to its duration range. That is to say, the duration can be increased until the closing flank of the cam lobe reaches the opening flank – a duration of 720 degrees. In a typical application the WHC would have a continuous duration range from about average for a road-going general purpose engine (say, about 250 degrees measured at normal valve clearance) to about 100 or 150 degrees above this. That is, from 250 degrees to 350/400 degrees.



The duration range of the WHC is accomplished in what most car enthusiasts or automotive engineers would agree is the “traditional” or most desirable manner a VVA (or variable duration) system should operate. The valve is opened at normal rates of acceleration, jerk, etc, and then held open at its maximum lift for whatever duration is required before being closed at a normal rate. No matter how short or how long the duration, the opening and closing rates are always unchanged. Another surprising thing here is that this style of duration change over a very wide range has never, in the very long history of the internal combustion engine, been achieved before by a mechanical VVA system no matter how complex or expensive. The only other arrangement that can rival this for width of range is a system where the lobes on two closely-spaced separate camshafts are bridged by a pivoting lifter which operates the valve. The basic idea being that one camshaft opens the valve and the other camshaft looks after the closing of the valve. Changing the relative phase of the two camshafts has the effect of changing the opening duration of the valve. This works well enough but at long durations the lobe on one camshaft may reach full lift before the other even starts to move the follower. This has the effect of halving the full lobe lift (and rate of lift) of each camshaft, at long durations the valve lift (and rate of lift) is somewhat lacking. In most applications the valve lift needs to be at a maximum especially at long durations.

Needless to say this is another of the very old existing ideas which are at regular intervals dug up and proposed as a “new” idea. Recently it has been revived in an arrangement where the two camshafts are combined in the one coaxial shaft with a rocking follower acting on the separate cam lobes. Although more compact than the two separate camshafts layout it still has the same limitations – perhaps even more so.

Mechanism

Although in essence a quite simple idea, to describe the actual mechanism and its operation is almost beyond the power of the written word. Even when held in the hands and worked through its duration range it can be difficult to understand just what is happening and how the WHC generates its continuous range of profiles. The mechanism of the WHC is a coaxial shaft arrangement where the outer shaft carries the main body of the cam lobe. The main body of the cam lobe is in its maximum duration shape (or profile) form. Typically the main lobe body would have a duration of about 400 degrees. The lobe is very long axially, about 45mm, and its profile consists of conventional opening and closing flanks separated by about 170 degrees of constant radius over the nose of the lobe. The lobe has a helical slot machined into it that has a helix angle of about 35 degrees relative to the rotational axis of the camshaft. The width of the slot is equal to the angular extent of the closing flank of the lobe. One edge of the slot extends diagonally the full length of the lobe across the 170 degree constant nose radius. The other edge is ground so that it is all at base circle level. The slot in fact replaces the closing flank on the main body of the cam lobe. Bridging the slot is a segment of lobe (about 10mm in thickness) which is ground to the profile of the closing flank. The segment is attached to the inner shaft. One edge of the slot has a constant cylindrical radius, the same radius as the lobe’s nose radius. The other edge has the radius of the lobe’s base circle. A small region along each edge of the closing flank segment has the same constant radius as the edge of the slot that it is adjacent to. This means the segment can be positioned anywhere along the helical slot and there will always be a smooth transition for the follower to and from the segment. The lobe segment is fixed to the inner shaft so any relative axial movement has the effect of changing the valve opening duration. The follower is arranged so that it always remains aligned with the segment which remains stationary axially. As the slot has a helix angle of about 35 degrees, any axial movement of the outer shaft causes the segment to rotate, exposing more or less of the nose constant radius and thus changing the duration. Make sense? Maybe not. This somewhat tortuous and convoluted explanation disguises the fact that the WHC is actually quite a simple mechanism. This brief description is not the entire story and more details, drawings etc. are available online on the USPTO website – the patent number is 6832586. The slightly indescribable and mind-boggling way it operates probably accounts for the fact that the helical movement principle has never been suggested before let alone built and run in an engine. New mechanisms, even minor detail ones, are almost unheard of – the WHC is a distinct contrast to the literally thousands of VVA designs in the USPTO files alone.

Cam Profile

The base or shortest duration profile of the WHC system is almost identical to a standard production engine profile. The WHC base profile belongs to the general group of lobe shapes which are used with pivoting cam followers – especially those with a fairly high rocker ratio. This family of lobe profiles are characterised primarily by not having a very great actual lift directly at the lobe (usually referred to as “lobe lift”). The lobe lift is enlarged by the rocker ratio which often is around 2:1 resulting in quite high lift at the valve. As the duration etc. is as for a normal lobe this results in the nose of the lobe having a very rounded-off (or “snub-nosed”) appearance. The radius of curvature of the nose region (about the axis of rotation of the camshaft) is often very close to being a constant radius over an angular extent of about 20 degrees or so. The WHC principle requires that this 20 degree region is modified to make it a true constant radius. In some cases this requires as little as 0.25mm (or less) to be removed from the nose. The constant radius area is then blended - in to the curvature of the standard opening and closing flanks.

Generally speaking, the modified minimum duration profile is identical in appearance to the standard profile – at least to the naked eye. When measured very accurately, the rates of acceleration, jerk etc. in the nose region are slightly higher than standard but only marginally higher. The WHC expands the duration by adding to the nose constant radius area and removing an equal amount from the base circle constant radius. The 20 degree constant radius area on the lobe nose typically can have about 150 degrees added to it. The 150 degrees is the extra duration. In effect, the opening and closing flanks “open up” exposing progressively more and more constant radius on the lobe nose. As both flanks are unchanged, the rates of lift/acceleration etc. and the total lift are also unchanged – no matter how much constant radius is added to the nose.

A critical question– is this the best way of making a longer duration profile? With the WHC the question is not entirely relevant. The intention is not to use the WHC principle to obtain a “fixed” profile but to develop a minimum duration profile that best suits a cam with totally variable duration control – which is something quite different. If the profile was for a conventional non-varying cam the answer would have to be “probably not”. It would certainly make a quite useable cam but not a really good cam. Certainly in the past, some long duration cams were made exactly in this way – by “opening-up” a standard profile. Even at present many racing cams are made this fashion (or at least with a lot of constant radius on the nose) for some oval track competitions in the USA. In certain classes the valve lift has to conform to the “limited lift rule” – even some very long duration cams. This results in a very distinctive “flat” region on the peak of the lift curve graphs of the cams. These “lift rule” cams rev to high RPM as well (or better) than more conventional racing cams. Usually with a high performance cam the lift is increased, the point being to get more flow into the cylinder. High performance cams generally have greater lift and greater rates of opening and closing of the valve. The aim is to maximise the cylinder filling while keeping the duration as short as is feasible. Keeping the duration as short as possible assists in retaining the lower RPM performance. In a sense the amount of lift/rate of lift etc. can be “traded” against the valve opening duration. If, for a particular application, lower RPM performance is not very important the amount of lift etc. can be kept at moderate levels and the duration increased. That is; the lift etc. and duration are roughly inversely proportional to each other.

This is the situation to some extent with engines driving water or air propellers, the engine more-or-less running at constant speed. With wheeled vehicles, no matter what the application, generally there is some need to restrain the amount of duration to retain at least some lower RPM performance. Even in racing, most types of race are standing start or if not still require accelerating from rest after pit stops, slow corners etc. The situation with the WHC is totally different. Even with an engine that must retain a lot of low RPM performance the maximum amount of duration that can be used is not restricted – it can be literally whatever is needed to produce maximum power at the maximum RPM the engine is capable. The implication would seem to be that both the rates of lift and the total lift need not be so high with the WHC.

This is a situation that cam designers have never really had to consider – there was no point in thinking about what having total freedom of duration choice would mean to the required lift, etc, if there was no mechanism available to allow wide range variable duration. If the WHC was forced to operate at the one fixed duration setting it probably would not be quite as good in performance as the best conventional cam of the same duration – but it would be far from being bad.

However, the fact that the WHC has an almost unrestricted duration range really makes it far superior to any conventional “fixed lobe shape” cam. It is almost a case of “in the land of the blind, the one-eyed man is king”. Having unlimited variable duration is an enormous advantage to a camshaft. An interesting aside here is that the style of profile generation and variable valve opening of the WHC is virtually identical to that of most hydraulic/electromagnetic “camless” systems as is its range of full-lift durations. This would seem to imply that there would be little point in using a “camless” system. The WHC can do the same sort of things but is much simpler, cheaper, more reliable and is not rev-limited (and does actually exist in a more-or-less production practical form – unlike the “camless”).

Applications

The “traditional” application of VVA (especially variable duration) is to match the engine RPM to the valve opening duration (this is very roughly what the VTEC does). The general idea being to improve the high RPM performance without the associated problems of a long duration “racing” cam which are lack of lower RPM power, rough idle, etc. Engines typically need a roughly linear increase in duration as the RPM rises. The aim is to maximise the torque at every point in the allowable RPM range. This means that with the WHC the old concept of a maximum power point in an RPM range no longer applies. The WHC employs a totally standard pivoting (or “finger”) follower and the whole WHC system is not rev-limited – or at least no more than any other finger follower layout. As most Formula 1 engines use finger followers it would seem that this type of follower does not hinder high RPM too much. This is in distinct contrast to most other VVA arrangements – “camless” included. With the WHC the power continues to build until the “breathing” limit of the induction system is reached – or more likely, the mechanical strength limit of the engine’s connecting rods, etc is reached. The WHC’s typical 250 degree to 350 + degree duration range basically means that a suitably robust engine could “pull” strongly from about 1500 RPM to maybe 20,000 + RPM and still idle smoothly at, say, 500 or 600 RPM.

This is not just “in theory” speculation. If you have a VVA system with an unlimited duration range and the VVA system is not rev-limited, then the type of performance just described would be quite possible. It is probably not well-known that competition engines that are intended for ultimate power output at extreme RPM (like Formula 1 or MotoGP) are still slightly limited in how long a valve opening duration they can use – they could actually make more power with even longer duration cams. As with lesser engines, consideration has to be given to lower RPM performance and power delivery characteristics. In a word, the car or bike (bikes especially) must remain at least reasonably “driveable”. Most of these engines are right on the limit of manageability (- if you can call F1’s 3000 RPM idle and no power under 10,000 RPM even vaguely manageable by most standards). For an engine intended for competition only, the idea could be expanded to possibly even a rev limit of maybe 30,000 + RPM as there would be fewer worries about “driveability” with the WHC. (As a point of interest, some small capacity competition two-stroke engines can run to well over 40,000 RPM so astronomical RPM levels are not unknown).



To repeat what has been said above; there has never been a mechanical VVA system that had either the duration range at full lift or the high RPM capability to do anything like this. “Camless” electromagnetic/hydraulic systems do have similar duration/lift ranges to the WHC but at present their high RPM ability is strictly limited.

On a possibly somewhat more practical level, dynamometer testing of road engines has shown that even with the WHC limited to only about 30 degrees increase in duration, a typical road engine can increase its power by 25% to 30% at the same RPM power peak as the standard cam – and the idle and low RPM behaviour are totally normal (which, of course, is one of the main points of VVA and the WHC).

Efficiency

In these days of extreme oil prices, the application of the WHC in its fuel saving guise is possibly an even more important application than just to maximise the power output of an engine. Testing of a WHC prototype in a Suzuki GSX 250 cc engine has a shown a remarkable improvement in fuel economy at idle speeds. This particular WHC is arranged so that all the duration increase is on the closing side of the intake cam lobe, the opening point of the intake valve remaining as standard on a Suzuki GSX 250 engine. The object of this was to test the effectiveness of LIVC on the idle fuel consumption.



The basic aim of LIVC is to reduce the intake pumping losses. These pumping losses are greatest at idle, progressively reducing as the manifold pressure (and the power output) increases. The test Suzuki engine consistently recorded a slightly startling 40% improvement in economy at idle when compared to the same engine with the standard camshaft fitted. This may seem a little unlikely, but it should be remembered that it has been estimated that at idle about 80% of the fuel used is just to overcome the intake pumping losses. Any reduction in pumping losses thus has a major and direct effect on the idle fuel use. As the power output rises, the 40% would quickly drop away but for an engine in typical road/traffic use an overall figure would be probably between 10% to 20% improvement.



The Suzuki idled at about 55 or 60 extra degrees of late closing. That is; about 120 degrees after bottom dead centre. This means that the total duration required was around 320 degrees. Engine load control by LIVC needs very long durations. Usually a much longer duration is needed for load control by LIVC than would be needed for high RPM power, especially for a general-purpose road-going application. Importantly all this very long valve opening duration, when used for LIVC, must be at full valve lift. The valve lift must be at a maximum so as not to impede the flow into and out of the cylinder. Any restriction to the flow causes pumping losses which defeats the whole purpose of LIVC. Needless to say, the WHC is the only mechanical VVA system that exists (or has ever existed) that has a wide enough continuous duration range to properly allow LIVC.



Having discussed the use of the WHC to aid high RPM power and also for load control by LIVC it should be made clear that there is no reason why both functions could not be used in the same engine. Realistically the WHC principle can only be applied to twin cam engines. For maximising power output both the intake and exhaust cam would need to be of the WHC type. The increase in duration needed for high RPM performance needs to be roughly equal on both the intake and exhaust cams, and roughly a symmetrical increase about the base duration lobe profile centre line. For LIVC operation alone, only the intake camshaft needs to be a WHC. With a twin WHC arrangement and suitable controls, an engine could have both extreme power output and also be very fuel efficient.

There is also the possibility of even greater fuel efficiency at the expense of outright power. The WHC and the general principle of LIVC also allow the possible use of a very high compression ratio (CR). The idea here being to use a very high geometrical CR but limit the compression pressure by LIVC so as to avoid detonation. The expansion ratio after combustion still remains high. It is the expansion ratio that fundamentally converts the heat energy of the burning fuel/air mixture into useable mechanical energy. The more the hot gases are expanded by the moving piston the more the heat energy is converted into useful work and the higher the thermal efficiency is. This general principle is usually called the “Atkinson Cycle”. (Strictly speaking the Atkinson Cycle refers to an engine with mechanically different length compression and expansion strokes.

In modern practice, the compression pressure is limited by a fixed amount of intake valve late closing - this has exactly the same effect as the different stroke lengths). With the Atkinson Cycle the added efficiency is at the expense of reduced overall power. For example, if an engine had a geometrical CR of 18:1 it would have to be restricted to about half its full charge of air/fuel mixture to avoid detonation. The resulting effect would be that at full load the engine would use half the fuel but the power would be not half but roughly two-thirds or three quarters that of the equivalent “normal” engine – the net result being an increase in thermal efficiency. Such an engine would be economical but it would still suffer from intake pumping losses.

The WHC would allow both the Atkinson Cycle and LIVC to be applied simultaneously. The high CR would allow even greater amount of LIVC to be used at idle thus further reducing pumping losses and improving efficiency. The resulting engine would have a fuel economy very similar to (or better than) a diesel – and it could run on the cheaper LPG fuel. It would also be lighter in weight and cheaper to make than a diesel. A car fitted with such an engine would appear to be a much simpler and cheaper alternative to a “hybrid” car. (But a hybrid fitted with a WHC/Atkinson/LIVC engine would be more economical still).

One of the more recent “fashionable” areas of engine research at present is the Homogenous Charge Compression Ignition (or HCCI) engine. It amounts to running a spark ignition engine at light or part load in a similar fashion to a diesel engine. HCCI requires the compression pressure to be very quickly and accurately altered so that the more-or-less controlled compression ignition doesn’t suddenly blossom into full-blown detonation. One of the main strengths of the WHC is that it can do exactly that. However, it would seem that the easily-controlled LIVC (with or without Atkinson high CR effects) is a much simpler way to control an engine than the decidedly risky HCCI process – and it is doubtful that HCCI is more fuel-efficient than LIVC, etc.

Operation

The duration of the WHC is changed by moving the outer shaft of the coaxial arrangement in a lengthwise (or axial) direction. The helix angle of the WHC is probably always going to be around the 30 to 35 degree mark. This translates to a figure of around 3.5 (crankshaft) degrees per millimetre of axial movement. 30mm of movement would give 105 degrees of duration change. Although the WHC is capable of far more than this, it has been found in testing that this amount is sufficient for most purposes. Little force is needed to move the shaft axially so there is a possibility that when using the WHC for LIVC load control alone the axial movement could be connected directly and mechanically to the accelerator pedal. Similarly, if the WHC is used to improve high RPM power only a simple self-contained (that is; it does not need an additional power source) centrifugal controller/actuator could be used. Some prototypes have run very well using centrifugal controller/actuators. If it was desired to operate the WHC to use both the LIVC and the high RPM aspects of the cam it would probably require hydraulic actuators on each cam (of a twin-WHC layout) to enable the LIVC to be used. Each WHC would also need a phase-changing mechanism for the high RPM use. At low RPM and part-load the WHC would be all LIVC. At high RPM and full load it would still require long duration from the WHC but the phase changing mechanism would need to alter the all-on-the-closing-flank duration increase to something of a more symmetrical duration increase. All this possibly could be done mechanically but the sensible arrangement probably would be an externally-powered arrangement with a computer/microprocessor to sort out the required amounts LIVC and phasing. For HCCI operation the picture is less clear but the very short (and thus very fast) axial movement that would be needed to change the compression pressure would seem to make the WHC very suitable for this process.


Considerations


One slight drawback (and maybe the only thing that could be called a possible problem) would seem to be the cost of the WHC. Even though it is a fairly simple device it requires very accurate helical machining and very careful assembly. The WHC prototypes typically cost about $1500 in machining and materials. This figure would reduce greatly in production. The cost of the WHC is really only high when considered in comparison to a conventional camshaft which reportedly cost the manufacturers only a few dollars per unit to make. This fact does tend to make the WHC look more expensive than it really is. Having said this, the cost of the WHC (and associated controls etc.) is probably very similar to (or even cheaper) than other production VVA systems.

The various prototypes have never shown any wear or ultimate strength (breakage) problems in the many hours of testing (some at very high RPM) they have undergone. But as a production car camshaft must ideally last for the life of the vehicle, there must remain some doubt until really long-term testing is carried out. However, indications are that there would probably be no insoluble long-term problems.

It probably doesn’t come into the category of a possible problem but realistically the WHC must operate through a lift-multiplying pivoting follower. The WHC could not really be used with an inverted bucket type of follower. Even though the inverted bucket is still used, it is being increasingly replaced both in road and racing engines by the pivoting “finger” follower. As well as needing a pivoting follower, if the engine has four valves per cylinder (and there are very few newly-designed engines that don’t) then the follower must be forked so that the one WHC lobe operates two valves. This is more a characteristic than a problem. If a really wide duration range is required, because axial space is somewhat limited along the camshaft, usually only room for one WHC lobe (and its operating space) can be found.

Also in the category of “not really a problem,” is the fact that the WHC does not “do” very short durations or variable lift. Many companies and manufacturers have made it appear that it is something of a virtue that their particular VVA system produces very short durations and the linked low valve lift as they really have had no choice. Up until the appearance of the WHC there was literally no method of mechanically producing continuous, wide-range full-lift variable duration valve timing. So it was either try to promote the reasonably-easily achieved short duration/low lift (usually by oscillating cam systems like the Valvetronic) or nothing. The long duration/full lift characteristics of the WHC are the commonsense way a VVA system should operate. It should be noted that there is no physical reason why a WHC could not be the “driving” cam in a Valvetronic-type oscillating cam setup. (But it would be quite complex and the Valvetronic part of the arrangement would limit the WHC’s high RPM capabilities).The result would be an almost unbelievable array of possible duration/lift combinations. This could be very useful in research.

However, in the real world probably 95% of the combinations have no really useful relevance to the four-stroke cycle. This, of course also applies to the WHC to some extent. What possible use could a duration of, say, 600 degrees be? It is hard to imagine a use for more than about 400 degrees – and the WHC potentially has another 300 or so degrees in hand. This is also true of the “camless” types. They have even greater duration ranges than the WHC but again, most of the range is just for novelty’s sake – it is not actually very useful. Besides this, “camless” VVA doesn’t really exist in any useable production form at present and may never do so.

The Williams Helical Camshaft would seem to have a bright future (and deservedly so). Most of its capabilities could be used to produce very fuel-efficient, powerful and cheaper engines. Oil prices will almost certainly never be low again, and the WHC has appeared just when it is most needed.

The WHC has one main obstacle to overcome. This is to convince engineers and the general public that for the first time in the entire history of the internal combustion engine a really effective system of mechanical wide-range, full-lift continuously variable valve opening duration has been discovered.

The WHC principle is one of the cleverest examples of mechanical lateral thinking that has been seen in many, many years.
taken from: http://www.helicalcamshaft.com

If this camshaft makes it into production, the aftermarket camshaft manufacturers will have a stiff competition to match already. Imagine being able to change the duration as well as the lift to match your engine setup.

Though this technology is up and coming for stock production bike, eg, Kawasaki's GTR14oo. It'll be still exciting for the aftermarket to get a taste of it on older engines.

06 April, 2009

Mat Mladin's GSXR 1000 K8 for Sale




This will be the final race weekend for Suzuki's 2008 GSX-R1000 in the hands of the Yosh lads. It can all be yours though ...

This just in:

Mat Mladin Race Bike for Sale
$59,000 USD
2008 GSX-R 1000
Mat Mladin Race bike:
Able to pick up from Road Atlanta after Race.


Engine Specs

  • AMA Superbike Spec Engine
  • Yoshimura camshafts
  • Yoshimura racing head gasket
  • Increased compression
  • Fully Ported and polished cylinder head
  • Yoshimura Race oil pan
  • Yoshimura Inner Rotor, Generator and Cover
  • Yoshimura Full Titanium Carbon Fiber R77 Exhaust system
  • EM Pro ECU with Race harness
  • BMC Racing air filter

Chassis Specs
  • Front Forks: Ohlins FGK pressurized internals
  • Brembo Mono-Block 4-Piston Calipers
  • 310mm Brembo Front Brake Rotors
  • Braided stainless steel brake lines
  • Yoshimura Triple Clamp, Offset / Caster assembly
  • Ohlins Steering Damper
  • Sharkskinz Fiberglass Cowling
  • Zero Gravity wind screen
  • JB Power Forged Magnesium wheels
  • Front 17 x 3.50
  • Rear 17 x 6.00
  • Ohlins TTX Shock
  • RK Chain, 520 racing chain
  • AFAM Sprocket
  • Galfer Rear Wave rotor
  • Motec ADL 2 Data logger / GPS, and Harness

03 April, 2009

Crower's 6-stroke engine

Briefly this is how a 6-stroke engine works:

The Crower six-stroke engine is a high-efficiency variant of an internal combustion engine under development by Bruce Crower.

Two extra strokes are added to the customary internal combustion engine four stroke Otto cycle, which makes a six stroke engine. A third down-stroke is a "steam stroke" and a third up-stroke exhausts the expanded steam while venting heat from the engine.

The engine cold starts on the Otto cycle, coasting through the fifth and sixth strokes for a short period. After the combustion chamber temperature reaches approximately 400 degrees Fahrenheit (200 °C), a mechanical operation phases in the fifth and sixth strokes. Just before the fifth stroke, water is injected directly into the hot combustion chamber via the engine's fuel injector pump, creating steam and another power stroke. The phase change from liquid to steam removes the excess heat of the combustion stroke forcing the piston down (a second power stroke). As a substantial portion of engine heat now leaves the cylinder in the form of steam, no cooling system radiator is required. Energy that is dissipated in conventional arrangements by the radiation cooling system has been converted into additional power strokes.

In Crower's prototype, the water for the steam portion of the cycle is consumed at a rate approximately equal to that of the fuel, but in production models, the steam will be recaptured in a condenser for re-use. Heat will be available from the condenser to provide interior heating of the vehicle, much as a conventional heater core works in cars and trucks today.
- article taken from wikipedia

The following is an article taken from Autoweek of an interview with Bruce Crower:

Bruce Crower has lived, breathed and built hot engines his whole life. Now he’s working on a cool one—one that harnesses normally-wasted heat energy by creating steam inside the combustion chamber, and using it to boost the engine’s power output and also to control its temperature.

“I’ve been trying to think how to capture radiator losses for over 30 years,” explains the veteran camshaft grinder and race engine builder. “One morning about 18 months ago I woke up, like from a dream, and I knew immediately that I had the answer.”

Hurrying to his comprehensively-equipped home workshop in the rural hills outside San Diego, he began drawing and machining parts, and installing them in a highly modified, single-cylinder industrial powerplant, a 12-hp diesel he converted to use gasoline. He bolted that to a test frame, poured equal amounts of fuel and water into twin tanks, and pulled the starter-rope.

“My first reaction was, ‘Gulp! It runs!’” the 75-year-old inventor remembers. “And then this ‘snow’ started falling on me. I thought, ‘What hath God wrought…’”

The “snow” was flakes of white paint blasted from the ceiling by the powerful pulses of exhaust gas and steam emitted from the open exhaust stack, which pointed straight up.

Over the following year Crower undertook a methodical development program, in particular trying out numerous variations in camshaft profiles and timing as he narrowed the operating parameters of his patented six-stroke cycle.

Recently he’s been trying variations of the double-lobe exhaust cams to delay and even eliminate the opening of the exhaust valve after the first power stroke, to “recompress” the combustion gasses and thus increase the force of the steam-stroke.

The engine has yet to operate against a load on a dyno, but his testing to date encourages Crower to expect that once he gets hard numbers, the engine will show normal levels of power on substantially less fuel, and without overheating.

“It’ll run for an hour and you can literally put your hand on it. It’s warm, yeah, but it’s not scorching hot. Any conventional engine running without a water jacket or fins, you couldn’t do that.”

Indeed, the test unit has no external cooling system—no water jacket, no water pump, no radiator; nothing. It does retain fins because it came with them, but Crower indicates the engine would be more efficient if he took the trouble to grind them off. He has discarded the original cooling fan.

So far he has used only gasoline, but Bruce believes a diesel-fueled test engine he is now constructing—with a hand-made billet head incorporating the one-third-speed camshaft—will realize the true potential of his concept.

Potential…and Questions

Crower invites us to imagine a car or truck (he speaks of a Bonneville streamliner, too) free of a radiator and its associated air ducting, fan, plumbing, coolant weight, etc.

“Especially an 18-wheeler, they’ve got that massive radiator that weighs 800, 1000 pounds. Not necessary,” he asserts. “In those big trucks, they look at payload as their bread and butter. If you get 1000 lb. or more off the truck…”

Offsetting that, of course, would be the need to carry large quantities of water, and water is heavier than gasoline or diesel oil. Preliminary estimates suggest a Crower cycle engine will use roughly as many gallons of water as fuel.

And Crower feels the water should be distilled, to prevent deposits inside the system, so a supply infrastructure will have to be created. (He uses rainwater in his testing.) Keeping the water from freezing will be another challenge.

But the inventor sees overriding benefits. “Can you imagine how much fuel goes into radiator losses every day in America? A good spark-ignition engine is about 24 percent efficient; ie., about 24 cents of your gasoline dollar ends up in power. The rest goes out in heat loss through the exhaust or radiator, and in driving the water pump and the fan and other friction losses.

“A good diesel is about 30 percent efficient, a good turbo diesel about 33 percent. But you still have radiators and heavy components, and fan losses are extremely high on a big diesel truck.”

Bottom-line, Bruce estimates his new operating cycle could improve a typical engine’s fuel consumption by 40 percent. He also anticipates that exhaust emissions may be greatly reduced. It’s all thanks to the steam.

“A lot of people don’t know that water expands 1600 times when it goes from liquid into steam. Sixteen hundred! This is why steam power is so good. But it’s dangerous…”

The danger of a boiler explosion has long been a factor in engineering—and in operating—steam powerplants of all kinds, and Crower is properly wary of the miniature boiler he has conjured up inside his test engine. That’s one reason he chose to use one originally manufactured as a diesel, for its inherent strength, though he installed a carburetor and ignition system so it could burn gasoline at first.

The original diesel fuel injector system now supplies the water spray to generate the steam-stroke.

In addition to producing extra power, the injected water cools the piston and exhaust valve, which suggests to Crower that he could raise the compression ratio. “I’ve done this many times on regular engines: 15-to-1 on gasoline for the first five seconds works pretty good until you get some chamber heat and then suddenly it gets into pinging. But with the chamber being chilled, I bet 12-, 13-to-1 will be no problem on cheap fuel.

“So what we can maybe do is have fuels that aren’t quite as good…It’ll save a nickel a gallon not having to keep three grades going.”

As for his hope of lowering emissions, Bruce speculates the steam might purge “cling-on hydrocarbons” out of the combustion chamber. “This thing may turn out to be so clean that you won’t have to have a catalytic converter.

But he admits that’s unknown, saying “there’s a lot of experimenting still to be done.” Which prospect makes him smile. He thrives on this kind of challenge.

Bruce’s Background

“You’ve kinda got to be in the cam business and know the dynamics of engines,” Bruce Crower says about how the idea occurred to him. And he certainly has that background.

He was building and racing hot rods (and hot bikes), manufacturing speed equipment and operating his own speed shop in his home town of Phoenix when he was still a teen.

After moving to San Diego in the 1950s, among other exploits he dropped a Hemi into a Hudson and drove it to a 157-mph speed record at Bonneville.

Inevitably, the inventive and inexhaustible Crower built up a major equipment business in superchargers, intake manifolds, clutches and, especially, camshafts. He’s also credited with first suggesting a rear wing to Don Garlits—in 1963, three years before Jim Hall’s winged Chaparral. Bruce Crower is now in Florida’s Drag Racing Hall of Fame.

Crower actually had introduced a wing two years earlier, during practice on Jim Rathmann's 1961 Indianapolis car—five years before Jim Hall’s winged Chaparral. Bruce had been crewing at the Speedway since 1954 (Jimmy Bryan, second place), and had been part of Rathmann's 1960 victory effort. He was likewise on the winning teams in 1966 (Graham Hill) and 1967 (AJ Foyt). Three decades later, in 1998, Eddie Cheever won with Crower cams.

Bruce even produced his own complete Indy engine, a flat-8 that didn’t quite make the field in 1977 and then was rendered obsolete (due to its width) by the advent of ground-effect tunnels. But the Crower 8 and its automatic clutch did win an SAE award for innovation.

Today, Crower Cams and Equipment Company employs about 160 people in five facilities, and manufactures not only cams but crankshafts and connecting rods—including titanium rods for (unnamed) Formula One customers.

Bruce Crower can’t be called retired now, but he’s happy to let the company he founded “roll along” while he “plays with cars.” That’s how he looks at the intensive R&D work he carries out in the privacy of his 13-acre horse property near the rural community of Jamul.

One of several projects is building up Honda S2000 engines for the Midget raced by his granddaughter, Ashley Swanson. (“I think she’s on par with Danica Patrick,” says the proud grampa.)

But his prime focus is proving his six-stroke engine is as revolutionary as he believes it is. “I’ve been trying to find something wrong with the whole basic idea for almost a year,” he says, “but I think we’re going to have a very marketable item.”

Then he adds philosophically, “If it turns out to be great, fine. If it doesn’t, it’s just another year out of my life that I’ve had a lot of fun doing something.”


If this engine makes it out onto the market, it'll be really exciting to see it running in front of you.

10 March, 2009

Spark Plugs - Some technical information

The following article is extracted from NGK's website. It explains quite clearly the different types of plugs and its applications. It's a good read for those considering making modifications to their engines. And also good to know for those who does their own plug changes.

Spark plugs are one of the most misunderstood components of an engine. Numerous questions have surfaced over the years, leaving many people confused.

This guide is designed to assist the technician, hobbyist, or race mechanics in understanding, using, and troubleshooting spark plugs. The information contained in this guide applies to all types of internal combustion engines.

Spark plugs are the "window" into the engine , and can be used as a valuable diagnostic tool. Like a patient's thermometer, the spark plug displays symptoms and conditions of the engine. The experienced tuner can analyze these symptoms to track down the root cause of many problems, or determine air/fuel ratios.

SPARK PLUG BASICS:
The spark plug has two primary functions:

  • Ignite air/fuel mixture
  • Transfer heat from the combustion chamber

Spark plugs carry electrical energy and turn fuel into working energy. A sufficient amount of voltage must be supplied by the ignition system to spark across the spark plug's gap. This is called "Electrical Performance."

The temperature of the spark plug's firing end must be kept low enough to prevent pre-ignition, but high enough to prevent fouling. This is called "Thermal Performance", and is determined by the heat range selected.

It's important to remember spark plugs do not create heat, they only remove heat. The spark plug works as a heat exchanger
by pulling unwanted thermal energy away from the combustion chamber, and transferring the heat to the engine's cooling
system. The heat range is defined as a plug's ability to dissipate heat.

The rate of heat transfer is determined by:

  • The insulator nose length
  • Gas volume around the insulator nose
  • The materials/construction of the center electrode and porcelain insulator

A spark plug's heat range has no relationship to the actual voltage transferred through the spark plug. Rather, the heat range is a measure of the spark plug's ability to remove heat from the combustion chamber. The heat range measurement is determined by several factors; the length of the ceramic center insulator nose and its' ability to absorb and transfer combustion heat, the material composition of the insulator and center electrode material.

Heat rating and heat flow path of NGK Spark Plugs

Heat Rating and Heat Flow Path

The insulator nose length is the distance from the firing tip of the insulator to the point where insulator meets the metal shell. Since the insulator tip is the hottest part of the spark plug, the tip temperature is a primary factor in pre-ignition and fouling. Whether the spark plugs are fitted in a lawnmower, boat, or a race car, the spark plug tip temperature must remain between 500C-850°C. If the tip temperature is lower than 500°C, the insulator area surrounding the center electrode will not be hot enough to burn off carbon and combustion chamber deposits. These accumulated deposits can result in spark plug fouling leading to misfire. If the tip temperature is higher than 850°C the spark plug will overheat which may cause the ceramic around the center electrode to blister and the electrodes to melt. This may lead to pre-ignition/detonation and expensive engine damage. In identical spark plug types, the difference from one heat range to the next is the ability to remove approximately 70°C to 100°C from the combustion chamber. A projected style spark plug firing tip temperature is increased by 10°C to 20°C.

Tip Temperature and Firing End Appearance

NGK Tip Temperature

The firing end appearance also depends on the spark plugs tip temperature. There are three basic diagnostic criteria for spark plugs: good, fouled and overheated. The borderline between the fouling and optimum operating regions (450° C ) is called the spark plug self-cleaning temperature. The temperature at this point is where the accumulated carbon and combustion deposits are burned off.

Keep in mind the insulator nose length is a determining factor in the heat range of a spark plug, the longer the insulator nose, the less heat is absorbed, and the further the heat must travel into the cylinder head water jackets. This means the plug has a higher internal temperature, and is said to be a hot plug. A hot spark plug maintains a higher internal operating temperature to burn off oil and carbon deposits, and has no relationship to spark quality or intensity.

Conversely, a cold spark plug has a shorter insulator nose and absorbs more combustion chamber heat. This heat travels a shorter distance, and allows the plug to operate at a lower internal temperature. A colder heat range is necessary when the engine is modified for performance, subjected to heavy loads, or is run at a high rpm for a significant period of time. Colder spark plugs remove heat quicker, reducing the chance of pre-ignition/detonation. Failure to use a cooler heat range in a modified application can lead to spark plug failure and severe engine damage.

Below is a list of external influences on a spark plug's operating temperature. The following symptoms or conditions may have an effect on the actual temperature of the spark plug. The spark plug cannot create these conditions, but it must be able to cope with the levels of heat...if not, the performance will suffer and engine damage can occur.

Air/Fuel Mixtures seriously affect engine performance and spark plug operating temperatures.

  • Rich air/fuel mixtures cause tip temperature to drop, causing fouling and poor driveability
  • Lean air/fuel mixtures cause plug tip and cylinder temperature to increase, resulting in pre-ignition, detonation, and possibly serious spark plug and engine damage
  • It is important to read spark plugs many times during the tuning process to achieve the optimum air/ fuel mixture

Higher Compression Ratios/Forced Induction will elevate spark plug tip and in-cylinder temperatures

  • Compression can be increased by performing any one of the following modifications:

    a) reducing combustion chamber volume (i.e.: domed pistons, smaller chamber heads, mill ing heads, etc.)

    b) adding forced induction (Nitrous, Turbocharging or Supercharging)

    c) camshaft change
  • As compression increases, a colder heat range plug, higher fuel octane, and careful attention to ignition timing and air/fuel ratios are necessary. Failure to select a colder spark plug can lead to spark plug/engine damage

Advancing Ignition Timing

  • Advancing ignition timing by 10° causes tip temperature to increase by approx. 70°-100° C

Engine Speed and Load

  • Increases in firing-end temperature are proportional to engine speed and load. When traveling at a consistent high rate of speed, or carrying/pushing very heavy loads, a colder heat range spark plug should be installed

Ambient Air Temperature

  • As air temperature falls, air density/air volume becomes greater, resulting in leaner air/fuel mixtures.
  • This creates higher cylinder pressures/temperatures and causes an increase in the spark plug's tip temperature. So, fuel delivery should be increased.
  • As temperature increases, air density decreases, as does intake volume, fuel delivery should be decreased

Humidity

  • As humidity increases, air intake volume decreases
  • Result is lower combustion pressures and temperatures, causing a decrease in the spark plug's temperature and a reduction in available power.
  • Air/fuel mixture should be leaner, depending upon ambient temperature.

Barometric Pressure/Altitude

  • Also affects the spark plug's tip temperature
  • The higher the altitude, the lower cylinder pressure becomes. As the cylinder temperature decreases, so does the plugs tip temperature
  • Many mechanics attempt to "chase" tuning by changing spark plug heat ranges
  • The real answer is to adjust air/fuel mixtures by rejetting in an effort to put more air back into the engine

Types of Abnormal Combustion

Pre-ignition

  • Defined as: ignition of the air/fuel mixture before the pre-set ignition timing mark
  • Caused by hot spots in the combustion chamber...can be caused
    (or amplified) by over advanced timing, too hot a spark plug, low octane fuel, lean air/fuel mixture, too high compression, or insufficient engine cooling
  • A change to a higher octane fuel, a colder plug, richer fuel mixture,
    or lower compression may be in order
  • You may also need to retard ignition timing, and check vehicle's cooling system
  • Pre-ignition usually leads to detonation; pre-ignition an detonation are two separate events

Detonation

  • The spark plug's worst enemy! (Besides fouling)
  • Can break insulators or break off ground electrodes
  • Pre-ignition most often leads to detonation
  • Plug tip temperatures can spike to over 3000°F during the combustion process (in a racing engine)
  • Most frequently caused by hot spots in the combustion chamber.
    Hot spots will allow the air/fuel mixture to pre-ignite. As the piston is being forced upward by mechanical action of the connecting rod, the pre-ignited explosion will try to force the piston downward. If the piston can't go up (because of the force of the premature explosion) and it can't go down (because of the upward mo-tion of the connecting rod), the piston will rattle from side to side. The resulting shock wave causes an audible pinging sound. This is detonation.
  • Most of the damage than an engine sustains when "detonating" is from excessive heat
  • The spark plug is damaged by both the elevated temperatures and the accompanying shock wave, or concussion

Misfires

  • A spark plug is said to have misfired when enough voltage has not been delivered to light off all fuel present in the combustion chamber at the proper moment of the power stroke (a few degrees before top dead center)
  • A spark plug can deliver a weak spark (or no spark at all) for a variety of reasons...defective coil, too much compression with incorrect
    plug gap, dry fouled or wet fouled spark plugs, insufficient ignition timing, etc.
  • Slight misfires can cause a loss of performance for obvious reasons (if fuel is not lit, no energy is be-ing created)
  • Severe misfires will cause poor fuel economy, poor driveability, and can lead to engine damage

Fouling

  • Will occur when spark plug tip temperature is insufficient to burn off carbon, fuel, oil or other deposits
  • Will cause spark to leach to metal shell...no spark across plug gap will cause a misfire
  • Wet-fouled spark plugs must be changed...spark plugs will not fire
  • Dry-fouled spark plugs can sometimes be cleaned by bringing engine up to operating temperature
  • Before changing fouled spark plugs, be sure to eliminate root
    cause of fouling
- article taken from: http://www.ngksparkplugs.com

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