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                    Recollections of my meetings with Abner Doble in 1930
 
                           As recounted to Bill Lloyd on 13 - 19 September, 1999       
Athol Jonas
Mt. Roskill
Auckland 4
New Zealand
 
                                       My first glimpse of Abner Doble and E-24
 
I was born on 8th July, 1911 in Auckland, New Zealand.  As a young lad in the 1920’s I had a keen interest in steam cars and had read of the legendary cars manufactured by Abner Doble in San Francisco.  One day about 1930 I was greatly surprised to see one of these cars in Auckland city.  It was parked on the northern side of Vulcan Lane off Queen street, just a stone’s throw from where I occasionally helped my father in his accountancy practice.  I asked if he could photograph the car for me using his quarter plate camera and he did this on two different days with the car in the same place on both occasions.  I often saw the car in the same area and in the same parking spot over several months.  It was a pale yellow coupé with black mudguards and I noticed that the paint was blistered in a circular patch on the rear part of the front bonnet.  The license plate was 8-341 and on another occasion 171031.  The right hand window was partly down and a spectator once reached in and blew the horn.  I was immediately interested in the instruments and noticed the steam pressure was reading 600 psi on a small gauge.  I don’t remember the exact colour of the car interior but I do recall that the seat leather wasn’t black.  To find out more about the car I got in touch with my cousin Charlie Jonas who was a mattress manufacturer with an office in Lorne street.  He had built a small model steam locomotive and was active in the model engineering society.  Doble attended an exhibition of this society and there is a photo of Mrs. Doble beside my cousin’s locomotive.  He told me that Abner Doble was in New Zealand to supervise a joint venture with A&G Price at Thames for the manufacture of steam buses for the Auckland Transport Board and the White bus company at Thames.  He also thought that Doble was importing the fuel for his car.  It wasn’t running on petrol.  It had a very distinctive and seductive odour of oil and steam that only a steam car can have.  I believe it was running on diesel oil which was very difficult to get in those days.  It was proposed to run the buses on diesel, which was much cheaper than petrol.
 
Doble’s car E-24 was parked in a side road in the busiest part of Auckland and usually attracted a lot of attention.  I always had a close look at the car whenever I could and on one occasion I saw a tall and distinguished looking gentleman getting into it.  He had a fair complexion and was neatly dressed in city clothes with a felt hat.  He was noticeably stooped for a young man of about 35 and I immediately noticed a conspicuous and rather horrible scar that ran diagonally down one side of his face.  It came from eye level down to his jaw and looked like a bad piece of facial surgery that hadn’t been stitched.  It was particularly noticeable on his rather pallid features.  There were several theories - a far fetched one that it came from a sword duel but the more likely explanation subsequently given in an article in Light Steam Power was that it arose from a boiler explosion.  I am a pianist myself and instinctively look at a person’s hands when I first meet them.  I noticed that his hands were unmarked, not the hands of a manual worker.  He had the hands of a musician rather than a manual engineer.  I would have liked to speak to him but was only about 19 at the time and was too shy to approach him directly.  Fortunately the opportunity arrived by accident a little later.  On this first occasion I watched as he got into the car and I heard a soft, deep rumble as the burner ignited.  A faint blue haze came away from under the car and left a delightful odour of steam, oil and flue gases.  The car moved off silently, except that when it was about 20 feet away there was a sudden “crack” like the knock of a hammer on metal.  Neither my father nor I knew what this was at the time but I now realise that this was one of the high pressure relief valves discharging condensed water from the cylinders back to the water tank.  I watched with my father as the car moved away in almost total silence.  I had just had my first glimpse of one of the most famous engineers of the steam age.
 
                                                 Chauffeured by Abner Doble
 
A little later I had the opportunity of meeting Abner Doble in person and riding in his car.  I was in a garage in Chapel Square in Auckland city to see a home built steam car with a Locomobile engine owned by “Steam” Stewart.  H.H. Stewart had been a joint agent with the Treloar Milking Machine Co which had been the sole or primary agents for the Stanley Company some years before.  Stewart also had some connection with the Doble/Price venture and had received around £750.00 in commission for introducing Doble to Prices.  I was chatting to Mr. Stewart and Jim Lawler the garage owner in the enclosed garage office when Abner Doble wandered in.  He had parked his car in the street outside the garage and was apparently expecting to meet Stewart there because he said to him “I want to make an appointment with you for lunch.”  After a little discussion, Stewart introduced me to the first American I had ever met in the flesh.  I noticed his accent but nothing otherwise remarkable about his voice.  It was average, unhurried but business like.  He was neatly dressed in a business suit with his felt hat and was smoking a cigarette in a short holder, something I hadn’t seen before.  He and Stewart spoke on first name terms and when Abner was about to leave I took an indirect approach and hurriedly asked Stewart “Do you think he’d give me a lift?”  “Give him a ride!” said Stewart in a rather obliging tone, possibly using the opportunity as a convenient way of removing an over-enthusiastic teenager from the office.  Doble immediately agreed and we walked out towards the car.  But before we got there he stopped to look at the experimental steam chassis that Stewart had built and which was being stored in the garage.  “I like the idea of your single spoked steering wheel!” he joked at the hasty construction.  As I got into the right hand side of his left hand drive car I noticed a small white wire haired terrier occupying the shelf behind the single front seat.  These were fashionable at the time and someone had given it to him as a present.  My next impression as I lowered myself onto the single bench seat was something of a surprise when the cushion hissed at me.  I had never seen a pneumatic cushion before.  He switched on and we turned around.  He had been parked on the “wrong” or right hand side of the road.  The car moved to the end of the short Chapel Square with the Catholic church on our right and we turned left into Wyndham street, then eastwards down to Queen street where he turned right.  He stopped some distance up Queen Street, on the eastern side, directly in front of what was then the Auckland Savings Bank and said “I’ll be here for about 10 minutes.”  He then reached across me to shut the passenger’s window to prevent the dog from escaping and excused himself with the comment “Just so he won’t elude you.”  I definitely remember him using the elegant expression “elude”.  He went into the bank leaving me and the dog in charge of this remarkable machine.  I was careful not to touch anything.  He returned from the bank and we proceed up Queen street to the Wellesley street intersection, occupied by the traffic officer since there were no traffic lights at the time.  Abner leaned across me again and said to the officer “Can I go right round?”  There was no reply but we were waved around and he made a complete U-turn at the intersection, going around the officer.  “You’ve got a car to be proud of” I remarked as we gathered speed.  “Oh yes, it’s a fine car” he answered with justifiable pride.  I was a bit shy and asked what I feared might have been a silly question.  “Can you drive with the hand brake on?”  “Oh no, it’s just like a locomotive” he answered immediately.  But then he hesitated a moment and as an afterthought said “Oh yes you could ..” and added something that now escapes me.  It might have been “but it wouldn’t be desirable.”  We turned right into Quay street and he put on a short turn of speed along by the wharves.  There was a distinct and effortless surge of power which was most impressive, even though the conditions were too restrictive for anything more than about 40 mph.  He switched off the burner and said “We’re coasting now.”  Then a moment later he asked “How much further can I take you?”  When I replied that I was going to Upper Queen street he was somewhat surprised and quickly exclaimed “We’re getting further from Upper Queen street every moment!” but I was so taken with the unique experience that I just said “No, just keep going.”  We stopped a few moments later outside the Auckland premises of A&G Price on the left, about half a mile along Quay street.  As we pulled up he said “I shall be here for about an hour” and extended his hand in a courteous manner which indicated that my unique journey was at an end.  “Pleased to have met you Mr. Jonas” were his last words as he opened the door and stepped out.  I walked back to the Baptist Tabernacle where I had left my father’s car or my push bike after my organ practice from 8 to 9 am.  Not only had I willingly traveled well out of my way but my father was less than pleased to hear that I had also broken an appointment he had arranged for me with a potential employer, just when the depression was beginning to bite.  But any pangs of conscience were more than adequately recompensed.  At last I had had my first ride in a steam car and in all the world there was no greater steam car than the Doble and I had been chauffeured by none other than the deity Abner Doble himself.  It was like meeting the almighty.  I felt like the King of England had taken me on a tour of Buckingham Palace.
 
                                            My last meeting with Abner Doble
 
I met Abner Doble on one other occasion.  Possibly around August, 1930 my mother saw in the Table Talk column of the New Zealand Herald that Mr. and Mrs. Doble were now staying at the Grand Hotel in Prince’s street near the university.  I telephoned the hotel and asked to speak with Mr. Doble.  I was put through to him and asked if I might come down to see him.  He agreed and when I asked when could I come he replied “Right now.”  I wasted no time in getting there and found him and his wife sitting in chairs on the steps approaching the front door.  We had a pleasant conversation in which he mentioned that he didn’t like living in Auckland and preferred Thames.  Thames is a much smaller town.  In the same breath he mentioned that he enjoyed tennis.  I recall asking him about the burner and he spoke about the venturi but I didn’t really follow because I had never seen one.  I told him that I was hoping to make up a steam car from a Mobile engine that I had.  “You’ll find it damn hard!” he replied.  “What speed could I expect from it?” I asked him.  “Oh, about 25 miles per hour.”  He also suggested “Why don’t you go down to Hamilton and see Jim Trelor?  He’s got a lot of junk!”  He was alluding to Stanley material, for which he appeared to have little regard.  I asked if he could lend me any information but he said “It’s all packed up.”  He was very patient and gave me about 20 minutes to half an hour.  Then he ended the interview with the words “How much more can I tell you because I propose to take my wife out for an airing?”  I remember these exact words because I thought it was an unusual expression.  His wife had sat patiently throughout our discussions, saying virtually nothing.  I later heard from Stewart that she may not have been his wife.  Her name may have been Alene.  He mentioned that he was the hand brake on?”  “Oh no, it’s just like a locomotive” he answered immediately.  But then he hesitated a moment and as an afterthought said “Oh yes you could ..” and added something that now escapes me.  It might have been “but it wouldn’t be desirable.”  We turned right into Quay street and he put on a short turn of speed along by the wharves.  There was a distinct and effortless surge of power which was most impressive, even though the conditions were too restrictive for anything more than about 40 mph.  He switched off the burner and said “We’re coasting now.”  Then a moment later he asked “How much further can I take you?”  When I replied that I was going to Upper Queen street he was somewhat surprised and quickly exclaimed “We’re getting further from Upper Queen street every moment!” but I was so taken with the unique experience that I just said “No, just keep going.”  We stopped a few moments later outside the Auckland premises of A&G Price on the left, about half a mile along Quay street.  As we pulled up he said “I shall be here for about an hour” and extended his hand in a courteous manner which indicated that my unique journey was at an end.  “Pleased to have met you Mr. Jonas” were his last words as he opened the door and stepped out.  I walked back to the Baptist Tabernacle where I had left my father’s car or my push bike after my organ practice from 8 to 9 am.  Not only had I willingly traveled well out of my way but my father was less than pleased to hear that I had also broken an appointment he had arranged for me with a potential employer, just when the depression was beginning to bite.  But any pangs of conscience were more than adequately recompensed.  At last I had had my first ride in a steam car and in all the world there was no greater steam car than the Doble and I had been chauffeured by none other than the deity Abner Doble himself.  It was like meeting the almighty.  I felt like the King of England had taken me on a tour of Buckingham Palace.
 
                                                   The Doble Steam Buses
 
Since my ride with Abner Doble, I have ridden in eight other steam vehicles including the buses.  I had two rides on the buses, both on bus Number 10 as a fare paying passenger around Auckland.  Once was to Point Chevalier and later along Mountain Road past the grammar school, which I had attended just a couple of years before.  Only three complete bus units were built, all different in detail. The first was sold to the Auckland Transport Board, installed in a converted AEC bus as described and illustrated in the newspaper cutting.  This was the only bus I rode in.  They were all conversion units, although one had a special body built by Cousins & Cousins and ran the 70 or 80 miles from Auckland to Thames for about 3 months for the White company.  I saw this one once on the road coming from Auckland as I was returning from Thames.  This one had the auxiliary unit driven by a donkey engine behind the condenser rather than by shaft drive from the main engine.  I once owned the complete power plant out of this Thames bus and sold it to a Mr Alexander in Sydney in 1948 or early 1949.  I later went to Sydney on the Wanganella in 1949 to exchange a turbo booster unit from Number 10 bus for a White steam car engine.  I can’t recall his name.  He wrote to me about a pressure atomizing burner that he had designed and how he found it.
 
The number 10 bus appears in the newspaper photograph and is the one which had the most use.  This was the first bus I saw.  It had a forward driving control, half way over the boiler room.  I first saw it in Commerce street in the city, coming in to its terminus and was impressed by the silence of the bus as it made a U-turn in Commerce street.  Riding was equally smooth, with a faint sound from the exhaust but much quieter than the old AEC bus engine.  It had that subtle and attractive odour of steam and oil.  I later saw the Thames bus coming from Auckland toward Thames as I returned.  This Thames bus was sold to the Thames Authority, which was separate from the Auckland Transport Board that owned the Number 10 bus.  I later visited the Price works in Thames after the project had been terminated and took stereo photos of one of the chassis.  Everything lay there for some time, until Price had a big clean up, possibly when they became Cable Price.  Even Doble’s workshop and drawings were there. 
 
There were some problems with the buses because they were under-powered except that the third one, the Thames bus, had a bigger boiler.  It had an auxiliary engine to take some of the electrical load.  Jo Bell said that this took too much steam.  It went at 1,500 revs and sounded like a petrol engine working.  I think it was a little compound V-engine.  The failure of the project was a combination of the lack of performance and the depression.  Fuel economy with Number 10 bus was said to have been about the same as conventional buses but with cheaper fuel.
 
                                                 The fate of the steam buses
 
​The compensator came from the Number 10 bus unit and some other parts from this unit ended up in my Chev steam car.  I don’t recall if the third unit, the Thames bus, had a compensator.  The second unit was lying idle for about 9 years but no one bought it.  I don’t know what happened to that second unit.  A chap in Hamilton, a Mr. Grinter bought the Thames power unit and I bought it off him.  This is the one I sold to Alexander without ever taking delivery of it.  I bought it with the idea of reselling it.  I paid about 90 pounds for it and only saw it in pieces in the railway yards.  It was just the power unit.  I think the engine of the third unit, the Thames bus, went to a museum in the UK because I got a letter from them about it.
 
“Bo” Bollond at Thames bought my Stanley about 1945 after I stripped a lot of stuff off it.  He got Prices to put a bus engine into it.  I don’t know what bus engine this was.  Brian Rankine has this engine at the moment.  Bollond might have got one separately from Prices.  He is the one who cut the auxiliary unit in half.  Sadly, he eventually committed suicide by gassing himself, I believe as a result of women trouble.    
 
Jo Bell, one of the guys who was in charge of the mechanics on the bus project at Thames said he once had the use of Doble’s car (E-24) for a weekend.  If the project had continued he would have made the control boxes.  A relation of his appears in a group photograph of the works people.  At Gary Summerhayes’ prompting I wrote 48 pages of memoirs of my steam car experiences for the Model Engineering Society, now the Steam Engine Society.
 
I rode in Doble E-13 once in Christchurch when Alec Gudsell had it and remember being most impressed at the way it went through thick sand on a sandy road, like a locomotive pulling up hill.  Joe Bell, who had worked on the bus project, said there could have been a third Doble car brought in by a tourist but only briefly.  He had seen the word “Doble” on the back of an electrician’s jacket.

 Stanley Mixing Tube Fires by Pat Farrell (aka SSsssteamer) SACA
NW Steam Clinic September 27, 2019
​What are mixing tube fires? The mixing tubes of the Stanley steam car are where the vaporized fuel and atmospheric air mix to produce a combustible flame to fire above the burner grate. When the fire presents itself below the burner grate in the plenum, or in the mixing tubes below, that is not acceptable. This generally is called a mixing tube fire. What are the causes? Most common tube fires are started by a fire leak from around the burner to boiler seal. The pilot light inspection hole not being fire tight, as well as the super heater exit at the rear of the burner can also start mixing tube 
fires. A fuel flooded mixing tube fire is usually caused by a flooded burner. The flooded burner can
be flooded either by the main fuel jets, or by the pilot light being out causing raw fuel to build up in the mixing tubes and plenum. Mixing tube fires can also be started by forcing the burner too fast at firing up and flooding the burner with raw fuel. Instead, preheat well and build a slow hot fire. Tube fires can be caused by the fire dropping down out of the burner and into the plenum by the way of a cracked burner grate. The burner’s slots or its drilled holes can become too big and therefore dropping the fire down through them and into the plenum. A warped or heat damaged burner grate can be the cause for the over-sized slots. The burner grate’s plenum not being sealed tight enough around the burner grate, can also allow the fire to descend into the plenum. Flooding of the burner plenum can be caused by using too heavy of fuel for the too large of main jets being used. Thin your fuel with gasoline or reduce the size of your jets to help reduce fuel flooding. This flooding is also a problem found at higher elevations where the oxygen is thinner. Sometimes, old fuel will refuse to vaporize, and until that fuel is disposed of, the old fuel will be a problem. Partially plugged main jets can cause drooling that will accumulate creating flooding of the mixing tubes. Misaligned main fuel jets within the mixing tubes can flood a side of a mixing tube and thereby flooding the mixing tubes. Also a resulting fog of vaporized fuel blowing back outside of the mixing tube can result in a puddle of raw fuel and an eventual tube fi re. The main jets vapor spray should always do a perfect bull’s eye inside of the mixing tubes. What should be done? A roaring mixing tube fire should be extinguished as soon as possible to prevent further damage to the Stanley burner grate. The first thing to do is to eliminate the fuel source by turning off your main burner valve. If I have a roaring tube fire, I prefer to quickly pull off of the road and try to let the excess fuel burn itself off in a small flame. Continued driving fans the tube fire making it a hotter tube fi re and possibly doing excessive damage to your burner grate. Sometimes if my mixing tube fi re gets too large, I will use my Halon fire extinguished to keep the fire from getting too big and doing collateral damage. Never use a powdered fire extinguisher in your mixing tubes as that will plug your burner grate up solid with extinguisher powder. To resume firing properly, the excess fuel has to be burned off, so a smaller fire is encouraged into eliminating the excess fuel. If the burner has lost its fi re and it is blowing raw fuel fog into the air, turn the main fuel valve off immediately and drive until the fueled smoke screen has subsided and then pull over to relight the burner. The first lighting attempt is to light the fire from the top at the smoke bonnet’s access door. To prevent your body from being burned, stand upwind from the fuel vapor cloud when lighting. Next is to check your pilot light at the peek hole for being lit. Light the pilot light if it is still out. What is the collateral damage? Too much roaring burning of a mixing tube fire will eventually crack your burner grate. Plenum fires can also destroy all of your refractory materials located in your burner. Excessive tube
fires with fuel left uncontrolled can eventually burn your Stanley up. Always shut off your main fuel valve when leaving your Stanley unattended. Try to shut off your main fuel valve a quarter mile before arriving at your destination. That should clear out any stored fuel in your steam automatic system and prevent your main fuel from later cycling on and drooling fuel while the Stanley is parked. What can be done to continue driving while tube fi res persist? Sometimes while on the road, a quick fix for tube
fires is just not available. To survive this problem and to continue driving, these steps can be taken. Reduce your fuel pressure so as not to create too much internal pressure inside of the burner/plenum area. Reducing your fuel pressure to below 100 PSI can sometimes get you home. Get your Stanley rolling up to about 18 MPH or faster before slowly turning on your main fuel valve. This creates a draft so as to keep the fire burning above the burner grate and not in the plenum or mixing tubes. Some Stanley's have a stack blower that can be used to duplicate this need for a draft. Before using your main fuel valve, by using your firing up valve you can gently bring your fire temperature up to a good
firing rate following with firing with the main fuel valve. If your burner grates become sooted up from tube fires and it restricts the passage of the air/fuel vapor, remove your main fuel jets and if you have one, use your steam enema with full steam to clear your burner grate of any soot. I have also removed my smoke bonnet, and by blasting down each fire tube with an air nozzle, I cleared the sooted up the burner grate below of its blocking soot. Once I was in a blinding dust storm that blocked my burner grate with dust. My steam enema saved me that day too. Hopefully something in my above SSsssteamer experiences will help you in your steam car adventures. <

From bill Bill Lloyd  2011

​Only today I had actually made a start at sorting through all my own Dungog photos, apart from just picking out a few here and there – like the ones attached.  I still have hopes of making a disc of all my rally photos of the past decade, but something always seems to interrupt the process.  I’m sure it will happen, eventually.
 
The Model K was delivered here to Denistone in Sydney to give me more time to “bond” with it.  It’s been stone cold since it left Dungog, but we’ll be taking it out again on Friday so a couple of friends from the Road Steam Engine Association can have a ride and officially certify it for its annual club registration.  The Doble went back to Trevor’s for some new plumbing.  Trevor’s currently on holidays somewhere in central NSW for a few weeks.   I nearly killed myself getting ready for the rally.  Now I’m killing myself catching up afterwards.  One of my friends went to London on Sunday.  Another left for Japan today.  He asked if I wanted to go with him, as I did once in the past, but alas, I’ve used up all my leave points for a while.
 
I’ve asked the body people to get me the Model K paint colour code which Basil wanted, so please tell him it will be forthcoming in due course.  They’re currently working on the 1915 Detroit electric, which was dropped off in the same truck which then loaded the Model K for Dungog.  The Detroit springs and wheels need stiffening up in a few places, with powder coating on the wheels.  Incidentally, I made contact with your friend Don Davidson, first to buy a reproduction motor plate for the Detroit and then to see about having some Doble hub cap badges made.  I told him how much I had enjoyed both the articles you sent me about his Detroit and Stanley.
 
Best regards to you both
Bill

(SACA Board member Tim Nye, learning that I was planning a visit to the University of Michigan’s Buhr Shelving Facility, asked me to scan the following article.  It is an English translation of a Czech article, right at the end of WW2. It is fascinating in that the Czech engineers were running a stationary steam engine without cylinder lubrication, instead using carbon rings to seal the cylinders. Ed.)  
 
HIGH SPEED STEAM ENGINE WITHOUT LUBRICATION 
By H. Frank and J. Rais. (From VDI Seitschrift, Vol. 89, Nos. 5/6, February 3rd, 1945, pp.6466). 
 
(Translation appearing in The Engineer’s Digest, October, 1945   Vol. 2, No. 10.) 
 
A STEAM Engine to operate without cylinder lubrication has been designed and built by the Skoda Works (Czechoslovakia – Ed.) for a special purpose, where oil-free exhaust steam and highest economy at even partial loads are vital requirements. The engine was built for an output of 440 h.p., with live steam of 43 kg. per sq. cm. pressure and 380 deg. C. temperature, the back pressure being 7-9 kg. per sq.cm. 
 
(steam at 612 lbs. per sq. inch, 716 degrees F and 100-128 psi back pressure. This engine was briefly mentioned by Stan Jakuba in the April/May/June 2000 issue of the Bulletin.  He noted it had a water rate of 18.3 pounds per horsepower-hour. This poor water rate is undoubtedly due to the low expansion ratio responsible for the high back pressure. It’s almost certain this industrial engine was designed to produce a high back pressure so that the exhaust steam could be used in other industrial processes.  Ed.)
 
Aiming to secure oil-free exhaust from a reciprocator, the Skoda Works had carried out extensive experiments with regard to the use of carbon seals.  However, these experiments, conducted since 1935, had been confined to considerably lower pressures. Thus, when faced with the present task, a new approach to the problem had to be made. The new series of tests were concerned with finding the most suitable type of carbon material, most suitable, that is, with regard to mechanical strength, thermal expansion, wear, and ability to withstand high operating temperatures. The most suitable material for the piston and the piston rod had also to be ascertained. Furthermore, an existing engine was equipped with carbon seals in order to measure leakage and other data. Carbon is adversely affected by the presence of oil, a sticky mass being formed which exerts an abrasive action upon the piston rings and wears them down with great rapidity. Particular attention had therefore to be paid to preventing lubricating oil from the crank case, from reaching the carbon seals. In this respect the provision of duplex scraper rings with inter-drainage proved most helpful. These rings are now made of sintered iron in place of bronze, as hitherto used. 
 
(This section can be interpreted to mean that the piston was affixed to a piston rod which, in turn, was reciprocated by a crosshead. It’s impossible to speculate on whether it was single or   In this manner the crankshaft, connecting rod and crosshead could all be oil lubricated without fear of introducing oil to the carbon rings. Since the piston has no appreciable side loads, likely not even contacting the cylinder wall, no lubrication would be required for anything but the piston rings.  Ed.) 
 
Carbon is a very good material for sealing purposes and by no means inferior to a metallic seal provided the rubbing parts to be sealed are as hard as possible and have a mirror-type surface finish. Should this not be the case, carbon particles will lodge in any existing pores and wear of the carbon rings will be inevitable. 
 
A horizontal engine design had to be ruled out for reasons of cost, and a vertical design had therefore to be resorted to. A multi-cylinder design had to be chosen, since large size carbon seals are net feasible because of danger of breakage. It was, moreover, necessary to decide upon a single-acting engine type in order to eliminate the stuffing boxes. The specified engine output called for a six-cylinder design with a bore of 
199 mm. and a stroke of 200 mm., the engine speed being 750 r.p.m. This results in a mean piston speed of 5 m. per second, which is a high value hitherto rarely used in steam reciprocator practice.  
 
(bore of 7.835 inches, stroke of 7.874 inches at a speed of 984 feet per minute, similar to that of some Doble engines – Ed.) ​

(The magazine illustrations weren’t sometimes too clear.  The magazine was almost 70 years old and it’s possible that British wartime rationing didn’t help as regards paper and ink quality.  
The drawings have been either modified or replaced as possible. Absolute reliance on the images should not be taken as they are best interpretation.  Ed.) 
 
Upon removal of the cylinder head, the carbon rings (a), as shown in Fig. 1, are slipped over the piston (d) together with the ring carriers (b). Circular leaf springs (e) serve to press the carbon rings lightly against the wall (f) of the cylinder. The piston crown is connected with the piston rod by means of the bolts (h). As these bolts exhibited fissures after short time in service, they were subsequently replaced by longer ones. The method employed for sealing the valve spindles is outlined in Fig. 2. Here it will be seen that the carbon bush (b) serves both as guide for the spindle (a) and as first stage gland, the steam pressure being throttled to a certain extent by the labyrinth-action of the grooves provided in the carbon bush. Sealing of this carbon bush against the valve body is effected at top and bottom of the bush by means of the elastic copper packings (c), the required degree of compression being exerted by the threaded gland (d). ​

The stuffing box proper is constituted by the ring carriers (e)containing the carbon rings (f). Each of the latter is composed of three circular segments, the segments of adjacent rings being staggered by 60 deg. (Detailed section A-B in Fig. 2). The carbon segments are pressed against the valve spindle by means of the insular leaf springs (g). Furthermore, locating pins are provided to keep the carbon segments from rotating. In order to prevent the leakage of steam to atmosphere, distance piece (h) is inserted below the two topmost rings, this annular distance piece connecting with the back-pressure steam space by means of the duct (m). The two topmost carbon rings therefore act only as seals against the back pressure of the engine. In this way steam loss is kept to a minimum.  
​
The rings (i) and (k) act as oil wipers, with the leakage oil being led away through the opening (l).  
The mutual angular disposition of the six cranks of the engine crankshaft is indicated in Fig. 3. The connecting rods are forged and milled in order to keep their weight to a minimum. The big end bearings are made in cast steel halves, while the crosshead bearings are of the box type. The light metal crossheads have wrist pins of special bronze. The crank case is a single welded piece in order to avoid bolting the crank shaft bearings; the latter are bolted to pedestals enabling the withdrawal of the crankshaft to one side without lifting it. The cylindrical crosshead guides are made in halves and can be easily removed together with the crossheads through the openings provided in the engine casing. In the original engine the piston rods and certain other parts were made of stainless steel, but this precaution was later found to be unnecessary.  ​

The employment of a mechanical governor had to be ruled out because of the high engine speed and the large controlling forces required, and a pressure oil governor system was therefore adopted, as shown in Fig. 4. The pressure oil pump as well as the gear type lubricating oil pump are driven from the engine shaft.  
​
Referring to Fig. 4 it will be seen that the small fly-ball governor (b) acts upon the pilot valve (c) of the slave cylinder (d). Valve control is effected in a novel manner, there being a cut-off control lay-shaft in addition to the main lay-shaft. The admission valves (e) are controlled by the cams (g) and the exhaust valves by the cams (h). The main lay-shaft revolves at constant speed, while the angular position of the cut-off layshaft relative to the main lay-shaft can be adjusted by shifting the pinion (i) by the movement of the piston of slave cylinder (c). Electrical remote engine speed control is provided. The engine is equipped with lubricating oil and pressure oil coolers, oil filters, and an emergency governor with oil hydraulic operation of the throttle valve. A manually operated pressure oil pump to set up the required oil pressure for starting is also provided. Provision for the absorption of thermal  expansion is made at all vital points, including the steam piping. ​

The steam supply line from the boiler was laid out with a minimum of bends, a distributing header being provided close to the cylinders. From observations made at points of the live steam connections close to the admission valves, it was found that there prevailed a weak steam  oscillation of a frequency corresponding to the rotational speed of the engine. In addition to this, higher harmonics and a certain amount of non-harmonics were also found to prevail. The most suitable means for the suppression of these oscillations has not been found as yet. As the compression amounts to about two-thirds of the admission pressure, there also occurred a small amount of vibration of the admission valves, but this could be eliminated by changing the valve springs.  
Compared to a slow speed poppet-valve engine of equal power at 125 r.p.m., the present engine affords a saving in weight of some 60 per cent. At the end of August,1944, the engine had been in service for about 8,000 hours without showing any marked wear of the carbon rings. The amount of cylinder lubricating oil saved during this period amounts to more than 5,000 kg. The guaranteed specific steam consumption was 11.2 kg. per kW.-hr. (18.4 lbs. per h.p.-hr. -  Ed.) with a tolerance of +5 per cent, with a load of 410 h.p. This compares with a measured consumption of 11.95 kg. per kW. hr.,(19.6 lbs. per h.p.-hr. – Ed.) that is, +6.7 per cent in excess of the guaranteed consumption. From diagrams taken at a later date, it was, however, found that two cylinders showed insufficient compression owing to faulty adjustment of the valve control. It is therefore confidently expected that after proper adjustment has been made the guaranteed steam rate will be met without tolerance. The indicator diagrams reproduced in Figs. 5 and 6 were taken with an electrical indicator. They clearly show the resonant oscillations occurring during the admission period. ​

(A couple of notes seem worth mention. It mentions that the cylinder walls should be quite hard and as smooth as possible. This seems reasonable as graphite is soft and would wear away against an even mildly abrasive surface. Industrial hard chrome (not the stuff put on cars and motorcycles for the sake of being shiny) sounds like it might fit the bill, if polished.  To be clear, this would be the kind of chrome plated onto injection molds to reduce wear … and other such heavy-duty work. 
Hopefully the article has been of interest.  It would seem to follow that, if this approach worked on engine cylinders, it might also be valid for piston valves.  It becomes more debatable for slide valves given the pressure applied to the sealing surfaces.
  
After having slaved over a hot keyboard to put the article into a computer, and reworking some drawings, Tim Nye pointed out that that I had missed the fact that Josef Rais, one of the authors, had previously taken out patents on carbon piston rings and seal.  The US patent, which is probably the most easily accessed, was applied for in March of 1934 (originally April 21, 1933 in Czechoslovakia) and was granted on April 4, 1939. It carries the title “Packing  Ring for Sealing the Pistons and Piston Rods and was assigned to the Skoda Works in Pilsen, Prague, Czechoslovakia. I have to thank Tim for this observation, it brings the article into much clearer focus. Rais makes the case for his patent, as follows: 
“This invention relates to a new and improved type of packing ring for sealing the pistons and piston rods of reciprocating engines and machines using working cylinders and reciprocating pistons. The known constructions of engines and machines of this type suffer from the disadvantage that the packing members must of necessity be lubricated with some special lubricant supplied from without. This requirement results in a considerable increase in the cost of running, and expensive means are necessary for reducing the quantity of lubricating oiI to the minimum. In steam engines, the lubricating oil contaminates the exhaust steam, so that the latter cans not be used for certain purposes, since it contains excessively large quantities of oil. 

In the case of compressors, the lubricating oil can be caused to ignite. In consequence of the increased air temperature, thereby resulting in an explosion and hence the destruction of the entire machine. (When working with 5,000 psi air compressors, while in the Navy, we used special vegetable based oils for cylinder lubrication specifically to avoid these explosions.  Ed.) Furthermore, the coolers are apt to become fouled by the lubricating oil, so that a special oil eliminating device becomes necessary. In the case of compressors in which a lubricant other than oil is employed, the pistons must be provided with soft packing means, for example cups, which are, however, comparatively short lived. In the case of refrigerating machines also, the lubrication with oil, glycerine, and other lubricants often gives rise to troublesome disturbances. Similar inconveniences due to the necessity for lubrication occur in the case of internal combustion engines also.  

The present invention overcomes these drawbacks by virtue of the arrangement that the packing members of the pistons or piston rods, or of both, consist of rings of carbon, graphite, or similar frictionless self-lubricating material, which rings are so resiliently mounted relatively to spring metallic supporting or holding means, that the necessary radial resiliency is provided without any independent lubrication whatever.  

These carbon rings are inserted in metal holding bushes, both the ring of self-lubricating matter's and also the resilient metal holding means being cut through by a single cut, for the purpose of enabling the entire packing member to be resilient radially.  

The packing ring according to the invention is rendered particularly well able to withstand the strains and stresses to which it is subjected by virtue of the arrangement that the ring consists of two coaxial independent rings loosely mounted one upon the other.”   

Rais notes: “In the hitherto known constructions of packing rings of carbon, graphite, or similar material the ring is either divided into a plurality of segments or else is rigidly connected to a metallic base. The first mentioned principle of construction does not ensure a perfect seal nor a uniform pressure of the packing ring against the co-operating surface, whereas with the second principle of construction the Independent stressing of the carbon packing ring is prevented, and in addition detrimental stresses are transmitted from the underlying base to the carbon ring whereby either the connection between the carbon ring and the metallic underlying base or else the carbon ring itself is damaged.  

These disadvantages are overcome by the present invention, by virtue of the arrangement that the metallic ring is loosely inserted in the carbon ring, with possible locking against lateral displacement. In accordance with the invention, the packing ring may for this purpose consist of two coaxial and independent rings loosely mounted one upon the other. These two rings are mounted one upon the other without any rigid interconnection whatever, with the result that the resilient action of the metallic ring is uniformly transmitted to the carbon packing ring. The sealing action of a packing ring constructed in accordance with the invention can be increased or reduced as required in the various cases of utilizing the rings in machines by choosing suitable metallic resilient material for the production of the resilient metallic ring. The seating surface between the two rings can be cylindrical; but may with advantage be provided with one or more grooves of any desired cone figuration for the purpose of preventing axial displacement. Packing rings constructed in this manner permit of radial movement of the ring performing the packing function. In this case, however, if the grooves be of dovetail or other shape, it is necessary to provide such connection between carbon ring and metallic ring with an amount of play which admits of displacement within limits permitting of perfectly uniform resilience of the packing ring. 

The resilient packing ring according to the invention is cut through in a normal manner at one point on its periphery, the cut in the packing ring and that in the metallic ring but either coincident or in offset relation to each other.” 
​
The following illustrations are all derived from the patent, while the abbreviations in the table replace the number designations used to describe patent features (on the theory that it might be easier to remember MR stands for “metallic ring” rather than the number 13, or whatever). ​

Figure1 shows three rings installed in the piston while Fig. 2 describes the rings themselves. ​

Figures 9 and 10 consist of packing assemblies holding multiple carbon rings. ​

Figures 11 through 13 show pistons built up in segments, which serve to entrap the packing elements. The bushings are either a springy retainer or are backed by leaf or helical springs. The stops distribute the spring load against the bearing surface after the carbon rings have reached the worn in state. Thus, the springs are actually a temporary expedient used to break in the packing element. ​

Generally speaking, the above embodiments are used with split, built-up pistons. Figures 21 and 22 are designed to be installed into the groove of a solid piston.  Leaf springs underneath force the carbon ring against the cylinder walls while the stops are pins driven into holes drilled into the piston grooves from either the top or bottom of the piston.  The rings are made in halves and use tongue and groove joints to promote tightness. ​

Rais noted: “In accordance with the invention the packing ring may be constructed in such a manner that its resiliency in a radial sense is effected by metallic means provided beneath the ring.”  This implies that he understood the metallic ring would supply the resiliency required to hold the carbon packing in contact with the sealing surface but did not rule out the natural resiliency of the graphite itself. 
​  
Today, we might have a greater range of options.  At least two companies manufacture carbon materials engineered with an array of properties.  Graphitar products are manufactured by US Graphite in Saginaw, Michigan while Superior Graphite is headquartered in Chicago, Illinois.  
Superior Graphite has been in business since 1917 while US Graphite was a spinoff of the Wickes lumber business and was founded in 1895 to exploit then-recent graphite discoveries in Mexico. 
The following comes from the Superior Graphite website found at:  http://graphitescarbons.superiorgraphite.com/Asset/RGC-Brochure.pdf ​

(RGC stands for ‘Resilient Graphitic Composites’, Ed.) ​

 
                 The Development of a Steam Powered Motorcycle
​                                            PART ONE
The following article covers the basic design philosophy for an attempt at the land speed record for a steam powered motorcycle and perhaps the outright record for any steam powered vehicle.

As a starting place for a steam powered land speed record, a motorcycle is a terrible idea. The restricted space envelope and poor aero-dynamic characteristics make it the worst possible concept. However, not to be daunted that is what we chose. The decisive factor was  because we had this small Bower and Bell engine, which was an Abner Doble inspired design, it is too small for a car, but deserved to be used in something. Our love of motorbikes and the idea of a steam powered motorbike is more appealing to us than the ultimate record itself, we have used a Suzuki Hayabusa as the donor vehicle.

The basic formula pertaining to drag is: Drag = Cd x (1/2 x density of air x velocity2 x Area), where Cd is the co-efficient of drag and Area is the projected frontal area. As we can see, drag increases by the squared function of speed. The two most important factors that we can control in design space is frontal area and the Cd.

A motorbike has a relatively small frontal area, which is good,. However, even fully faired racing motorbikes struggle to achieve better than a Cd of 0.6. This compares to 0.3 for a modern road car, a Streamliner can have Cd as low as 0.12.​From the RSR Bonneville Aero-Horsepower & Drag Loss Calculator: available online at: - 
https://www.rbracing-rsr.com/aerohpcalc.html 

Coefficient of Drag: Street, faired motorcycles are notoriously inefficient aero-devices with Coefficient of Drag (Cd) figures in the 0.6 range. For example, a Suzuki Hayabusa has a Cd of .561 whereas a Kawasaki ZX-12 has a Cd of 0.603. Modern cars often have paid close attention to aerodynamics and may have Cd figures of 0.3. Streamliners may have Cd figures of under 0.2, perhaps as low as 0.15 or in some cases figures of 0.10 have been achieved.
 
Frontal Area: Reducing frontal area is key to going fast as the horsepower requirements go up exponentially as you push that "barn door" through the air. You'll need a close approximation of your vehicle's frontal area in square feet to make this calculator entry. A Suzuki Hayabusa has a frontal area of 6.01 square feet. A Kawasaki ZX-12 has a frontal area of 6.09 square feet. Some streamliners like the Lambky Vincent have only 4 square feet frontal area. 
​
Vehicle Weight: On shorter courses with asphalt surfaces and good traction weight is more of an issue than it is at Bonneville, where weight can aid traction on the slippery salt surface. Short courses are more of a drag race and accelerating extra mass is not a good idea. At Bonneville the big dogs will be on the long course with over six miles of salt with the clocks at the 2, 4, and 6-mile markers, so weight is not nearly as much of an issue.

                                 Figure 1: An example of a record setting Streamliner at Bonneville ​

                                      ​Figure 2: At Elvington airfield UK setting 80mph run

A mechanical water pump is fitted to the end of the free-wheeling hub output shaft. This delivers all of the water necessary. The capacity of the water pump is approximately 200% of theoretical demand, ensuring the ability to rapidly increase the water level within the steam generator if steam temperature is too high.
​The water pump is driven by an eccentric, which can be changed to provide different water delivery, should testing reveal changes are required. Water must be added to the steam generator at start up by external means, as no electrical or hand pump is provided on the bike.
 
We have chosen to run the steam generator at between 900 and 950 Fahrenheit. The steam lubricating oil limit is 1000F. This increase in temperature results in reduced water consumption for a given power. Abner Doble typically used 850lb/hr at 850F as the requirement for a 100Hp engine. This aligns with the water consumption predicted by my spreadsheet. 
                                                         Steam Generator 
The steam generator has been designed to output sufficient steam for 96Hp, which is 750lb/hr at 950F. The basis for all fluid velocities and required surface area has been calculated from the work of Abner Doble, including the required combustion volume. The steam generator has ~430 feet of 8mm OD tube for the water coils, 180 feet of 12mm OD tube for the steaming coils, 30 feet of ½ OD tube for the Normaliser and 30 feet of ½ OD tube for the super heater. The water and steaming coils are carbon steel for improved heat transfer properties. This minimizes the required tubing and the ​​Normaliser and Superheater coils are 316L stainless steel to withstand the higher temperatures. The total weight of tubing is 120lbs and the internal volume is 0.3 cubic feet. If one considers that the required output of 727lb/hr equals 12lb/min and the internal volume is sufficient for ~9.5lb of water/steam, then simplistically the approximate time that a molecule of water entering at the inlet to the generator takes to subsequently exit the generator at 950F is (9.5/12) *60 = 47.5 seconds. At full power the velocity in the water tubes is 9ft/ sec, in the steaming coils 50ft/sec and in the superheater 75 ft/sec. Therefore, notionally the water spends 48 seconds in the water coils, 3.6 seconds in the steaming coils and 0.8 of a second in the superheater. 
​
This might seem incredibly fast. However, comparing to Abner Doble’s design for a 100Hp generator producing 850lb/hr of steam at 1000psi, (steam at this temperature and pressure has a density of ~1.39lb/cubic foot). 

Producing 850/3600 = 0.236lb/sec. 
​
The super heater and normaliser coils are 3/4inch OD, 9/16inch ID and 39 feet total length. The cross-sectional area is therefore 0.2485inch2. The volume in the superheater is (39*0.2485/144) = 0.0673feet3, so contains 1.39*0.0673 = 0.0936lbs of steam. Therefore, to produce 0.235lb per second, requires the superheater to be emptied 0.235/0.0936 = 2.5 times per second, 2.5 times 39 is 98 feet per second velocity!

                                           Figure 4: Steam generator casing ​

                                                         Figure 5: Schematic of plumbing ​

                                                        Figure 7: 3 phase 24V EDF  ​

​Then the heat removed from the generator is simply the mass flow rate x the heat content.

​The generator efficiency is estimated from the relationship between mass flow rate/ heating surface area, the generator has been sized to achieve ~80% efficiency at full power. Since we now have a value for heat removed in BTU/hr the fuel demand is simply calculated from:

approximations within this approach, will be such that equilibrium is unlikely to be exactly achieved, as such temperature and pressure will rise or fall during operation in proportion to the errors within the calculations.
There are various permutations. However, in simplistic terms (for the sake of this article) there are four basic scenarios, temperature to low or too high, and pressure too low or too high.
1. If temperature is low but pressure is good, then there is excess water in the generator, i.e. the water to saturated steam transition is too high up the coils. The remedy is to reduce feed water input.
2. If temperature is too high but pressure is good, then there is excessive heat and insufficient water. The remedy is to reduce burner input, and increase feed water (a normaliser can be used to control excess temperature. However, additional feed water must also be added at the bottom end to remedy the situation.)
3. If pressure is low but temperature is good, then again there is insufficient water in the coils. The remedy is to increase feed water and heat together.
4. If pressure is high but temperature is good, then there is too much water in the coils. However, both water and fuel must be reduced together.
 
Formula for temperature and pressure correction factors have been created. These are used to bias the fuel demand and water delivery. Therefore, the initial fuel and water demand, which was calculated from heat/ steam being removed, is either increased or reduced according to the conditions in the steam generator relative to the operating set point.

Clearly if either the boiler efficiency or the steam usage is significantly out, then the system will find equilibrium away from the desired set point. Therefore, trim pots are provided on the control interface to allow the boiler efficiency and or the leakage factor to be adjusted to bring the convergence in line with the operating point. An error in efficiency would result in issues related to heat input, errors in steam usage would result in issues with feed water rate.

If steam usage was underestimated, then we will see an increase in temperature with a falling pressure. This is because there is a reducing water level in the generator. Therefore, the leakage factor must be increased. Should pressure be high and temperature low, then steam usage is overestimated and leakage factor should be reduced. Note the reduction in calculated steam removal has the effect of reducing both feed water and heat input proportionately. Therefore, pressure should reduce. However, temperature will be maintained via the reduced water level within the coils despite the proportional reduction in heat input.

Should boiler efficiency be underestimated then we will see over temperature and over pressure. In this case boiler efficiency factor should be increased, this will reduce the fuel delivery. Should temperature and pressure be low, then boiler efficiency has been over estimated and the boiler efficiency factor should be reduced, thus increasing fuel delivery.
So leakage factor increases or decreases feed water and fuel in proportion
Boiler efficiency either increases or decreases burner input alone. ​

​There are three control modes:
Minimum Burn:
At its lowest fuel pressure setting and with the return line fully open, the burner delivers approx. 1.2gal/hr. In this setting the burner cuts in and out at the operational point for pressure and or temperature, the fan continues to run at low speed to prevent a damaging heat soak, which could otherwise occur. The system stays in minimum burn, whilst demand is less than the minimum burn value (1.2gal/hr). Speeds in excess of 30mph will be required before demand exceeds minimum burn.

PRV control:
Once demand for fuel exceeds minimum burn mode, the system automatically switches to PRV control. Now the system varies the PRV position in the nozzle return line to match fuel delivery to demand. As the demand increases, the PRV progressively closes. The return flow meter is used to calculate fuel delivery. However, as the PRV approaches fully closed, the low flow starts to make the flow meter readings unreliable. As such, an algorithm is used to calculate return flow from PRV position at the final stages of closure. Unlike in minimum burn mode, the system modulates around the desired operating point. As previously described the fuel demand and water is modified based on generator conditions. Therefore, if pressure exceeds the operating point, this results in a reduction in fuel and feed water. The reduction progressively increases the further from the operating point the system gets. If this results in reducing steam temperature, then the feed water will be cut back further still. If the steam temperature actually rises due to the reduced feed water, then feed water is increased. Should the control system fail to keep the pressure and or temperature within the upper operating band around the set point, the system will drop into minimum burn mode. Once conditions return to within the operating band, the burner will ramp back up to the required demand again. Should, however, even minimum burn mode not prevent further pressure and or temperature rise, then upon reaching the safety limit the burner and feed water will fully shut down.

Speed Control mode:
Once fuel demand exceeds PRV mode, the return line valve and PRV are fully shut. Now fuel delivery is varied by increasing fuel pump speed. This has the effect of increasing fuel pressure in the fuel rail. Fuel pressure can be varied from 100 – 300 psi and at 300psi this gives 9.9g/hr. Modulation (including shut down) is as described for PRV control mode.

Feed Water control
The water pump is driven from the output shaft of the engine via the free-wheeling hub Therefore, even when coasting, the water pump is driven via the back wheel. However, no feed water is available when stationary. The outlet from the feed water pump has a recirculation line back to the inlet port of the pump via a solenoid valve. When this valve is open, no water is delivered to the generator. It is a simple task for the PLC to modulate the solenoid valve to control the proportion of water delivered. In addition, an offtake from the pump delivery goes to a second solenoid valve and from thence to the normaliser. Should the stem outlet temperature be too high, then the normaliser solenoid valve opens and allows cold water to injected to the top coils of the generator. The feed water entering at the bottom has an increased pressure compared to the steam leaving the generator at the top, due to the pressure drop related to velocity within the generator. As such the pressure delta increases with demand and so the fixed orifice in the normaliser nozzle has been sized to deliver approximately 10% of the feed water rate for any given speed and demand. The normalizer nozzle should consist of an orifice followed by approximately 3 inches of shroud within the steam main. This shroud is heated by the superheated steam. The water spray entering the shroud (via the orifice) is heated and turned to wet steam within the shroud before it mixes with the main steam flow, ensuring good mixing and efficient heat transfer between the gaseous fluids. If water is merely injected straight into the super heater coil, then the water droplets bead like water dropped on a hot plate and the effectiveness of the system is much reduced, (remember at full demand the velocity in the superheater is >75ft/sec), with a mix of wet and superheated steam leaving the generator outlet. The water pump is fixed displacement, thus the feed water rate is calculated from engine rpm and validated by a flow meter within the suction line to the pump. A non-return valve on the pump inlet ensures that when in bypass mode, the internal pressure in the pump is largely maintained and not just lost back to the water tank. An electric boost pump ensures that pump inlet conditions are maintained to prevent cavitation.

Part two will follow after further updates to design and testing.