IMPROVEMENTS IN SPLIT CYCLE INTERNAL COMBUSTION ENGINES

Abstract: A split cycle internal combustion spark ignition engine having a firing cylinder (10) and a compression cylinder (11) each with pistons connected to a common crankshaft. To enable spark ignition at a voltage giving acceptable spark plug life while retaining the advantages of high combustion chamber pressure is initially contained by admitting a pilot charge of fuel-air mixture at a pressure below 2000KPa, spark igniting the pilot charge at or near top dead centre and then, early in the power stroke, admitting a second charge of air-fuel mixture compressed to a pressure greater than 2000KPa for ignition by the burning pilot charge.

Description: Improvements in Split Cvcle Internal Combustion En g ines Technical Field This invention* relates to internal combustion engines in which compression is performed in compression cylinders maintained cold and combustion takes place in firing cylinders maintained hot, the compression and firing 5 cylinders being physically separated. Compression pistons and power pistons reciprocate respectively within the compression εnά firing cylinders, all of the pistons being connected to a common crankshaft. Each firing cylinder has minimal working clearance between the crown of the power -I Q piston and the cylinder head, which, together with recesses for the valves and the spark plug, define the combustion chamber. The unswept portion of the combustion chamber is accordingly of very small capacity. The pressure reached within the combustion chambers are greater than . j e those reached in engines operating on the Otto or diesel cycles. The engines of the above described construction are referred to hereinafter as " split cycle engines n . Background Art Split .cycle engines have been described in my U.S. Patents 20 Hoe, 3, 08,811 and 4,186,561. It has been found in practical experience with engines of the construction described in U.S. Patent 2To. 3,408,811 that the high gas pressures in the combustion chamber during ignition reσuire higher electrical potentials to be applied to spark plugs 25 than in conventional internal combustion engines, with the result that the working life of the spark plugs is shortened. U.S, Patent 2o. 4, 86,561 was directed to avoiding this difficulty by using ignition means other than spark 30 plugs. Sp&rk plugs, however, permit the timing of ignition in a particularly convenient manner, and equipment for use with them is already available on the market. Disclosure ot the Inventic.n It is accordingly the principal object of the present invention to provide a split cycle engine wherein combustion is initiated hy conventional spark plugs operating at electrical potentials sufficiently low to c ensure a spark plug life comparable frith the li e of the spark plugs used in conventional Otto cycle spark ignition engines. This requires a gas pressure at the time the spark passes of less than 2000 k?a. In order tα achieve this principal object, the -j Q present invention provides a spark i nition internal combustion engine comprising a firing cylinder and a compression cylinder having reciprocating therein respectively a power piston and a compression piston connected to a common crankshaft, a combustion chamber -j^ defined by the firing cylinder head, at least one recess containing valve heads and spark plug electrodes, and the crown of the moving ower piston, characterised by means directing into the combustion chamber in advance of the spark as the power piston approaches or reaches top dead 20 centre a pilot charge composed of- spark - ignitable fuel mixed with compressed air at a pressure below 2000 k?a, means producing a spark across the electrodes at or near top dead centre, and means directing into the combustion chamber after the sp rk and while the piston is moving 25 away from the cylinder head on the first part of the power stroke a second charge composed of fuel and air compressed to a pressure greater than 2000 k?a. he unique characteristics of split cycle engines can be exploited to assist deceleration of the engine when 30 by diverting the compressed air supplied by the compression cylinder away from the power cylinder, thereby reducing the pressure in the combustion chamber. The compressed air so diverted may conveniently be stored in a compressed air receiver, which to save weight and space may consist ot a honeycomb arrangement of hexagonal tubes joined together side by side to form structural members of a frame of a vehicle or other structure associated with the engine. The means directing compressed air into the combustion chamber may comprise at least one poppet valve closed by a compression spring bearing against a movable S top urged in the direction to close the valve by the pressure of the compressed air. The force required from the mechanism opening the valve is then less than would be required in the absence of this arrangement- One practical example of an engine according to the present invention -will now be described with, reference to the accompanying drawings. Brief Description of the Drawings Pig. is a schematic sectional view of the parts of the . engine with which the invention is concerned; Pig. 2 is a cross section on a larger scale of a component of the engine; ig * 3 is a cross section on line 5-5 of Pig. 1 on a larger scale; Pig. * is a cross section of a power piston; Pig. 5 is a cross section on a larger scale of the head of the compression cylinder; and Pig. β is a cross section on a larger scale of a further component of the engine. Best Mode of Carrying out the Invention He erring now to the drawings, the engine comprises a firing cylinder 10 and a three stage compressor 11, in this embodiment arranged in a Tee conformation and linked to a common crankshaft as desσribed--in U.S. Patent _Tσ.- If.,186,561 • A combustion chamber is constituted by the space de ined by the head of the iring cylinder 10 and the crown of the power piston 38 reciprocating therein, and recesses for the heads αf valves 17 and 3 and for the electrodes of a spark plug- 36• A branched pipe provided with, a non-return valve 13 leads from the high pressure stage 1iμ of the compressor to a two-way valve 15 * One outlet from the valve 15 is connected by pipe 1α to the top of the firing cylinder 10 through a pαppet valve 17- T e other outlet from the valve 15 opens into a pipe 18 opening into -a-pipe 19 leading from a compressed air storage receiver 20 into pipe 12 through a manually operated starter valve 21 and also into pipe 12 through a side branch 22 in which is located an air bleed valve 23 and a non-return valve 2i÷_ A pipe 25 leads from the intermediate stage of the compressor 11 to a pressure selector 26 through non- eturn valves 28 and 27. The pressure selector 26 is also connected to the pipe 22 and to a reducing valve 29 from which a pipe 30 leads to the iring cylinder 0 through a poppet valve 31 • The pressure of the air admitted to the firing cylinder 10 through the poppet valve 31 is maintained within the range at which spark ignition can be reliably performed with a conventional spark plug, for example 1100 k?a.. This is achieved by directing the air from the pressure selector 26 through the reducing valve 29 and the pipe 30 to the poppet valve 31 • The air emerging- from the pressure selector 26 is therefore at a pressure higher than the pressure. equired in the pipe 30. ua pressure selector 26 is shown in Pig. 2 and comprises a cylinder 32 closed at both ends having a discharge port 55 ■ permanently connected to the reducing valve 29 and a spring loaded piston 5 sliding in the cylinder 32, the 51 C..-.PI that the piston moves to place pipe 25 is communication wit port 33 if the pressure of air from the second, stage of the compressor is sufficient to compress the spring 55• If the pressure in the pipe 25 becomes insufficient to compress the spring, the piston 5 moves to the right to place pipe.22 in communication with port 33- a this way, the air supplied to the pipe 30 is drawn from pipe 12 and the high pressure stage 11+ of the compressor 11 rather than the intended normal arrangement in which the pipe 30 is supplied with air from the intermediate stage of the compressor. The air from the port 33 passes through the reducing valve 29, where its pressure is reduced to a constant pressure of approximately 1100 kPa, to the pipe 30 and the poppet valve 31 • When the engine is running normally, a constant volume of relatively volatile- pilot fuel, for example petrol, is injected by a fuel pump . not shown) into the air entering the firing cylinder 10 through the poppet valve 31 -■ as the firing piston approaches top dead centre, and the mixture is ignited hy a spark from a spark plug 3D before the piston reaches top dead centre. As shown in Pig. 3 > the electrodes of the spark plug ό and the head of the poppet valve 31 are both located in a shallow recess in- the head of the cylinder 10, and the head of the poppet valve 17 is located in a deeper recess also formed in the head of the cylinder 10. The pilot charge of air entering the cylinder through the valve 31 blows residual exhaust gases from the previous combustion. away from the vicinity of the spark plug .36, thus ensuring effective ignition of the pilot air and fuel mixture by the SOark. 6- While the pilot charge is burning, the poppet valve 31 closes and the main charge of air enters the cylinder 10 from pipe 2 throug the valve 15, pipe 1β and poppet valve 17. Because this main charge is at a pressure higher than that in the cylinder, its velocity may blσ*sr out the pilot flame unless the blast is deflected. To attain this it enters through a deep recess " so is directed away from the burning gases in the vicinity of the spark plug. The main fuel is injected into the compressed air shortly before it enters the cylinder 10 through the valve 17- The mixture is ignited " by the burning pilot charge, and burns with a sustained torch like flame to provide the main driving thrust in the cylinder 0. For maximum economy, the fuel pump injecting the main fuel may be arranged to reduce the rate of flow of main fuel over the concluding part of the injection. Secause of the ef ectiveness of ignition by the burning pilot-charge, the main fuel may be a cheap liquid of low volatility not usually considered suitable for use in spark ignited engines. If such a fuel is used, separate fuel tanks are provided for the main and pilot .fuels * A fuel pump 37 having a delivery variable in response to the changing pressure of air delivered through poppet valve 17 caused by the accelerator setting, or the load on the engine, supplies the main fuel to air entering through poppet valve 17 from pipe 12 * The fuel pump 37 may for example be of the construction sho * _n in Fig. 13 of U.S. Patent _To. Ij.,186,561, but its timing will not require the accuracy attained by the special cam follower shown therein. The performance of compression and firing in separate cylinders, which is a fundamental feature of split cycle engines^ permits a change in the construction of the power pistons. Whereas in conventional internal combustion engines it is essential that heat passed to the top of the piston from the hot combustion gases be conducted through c;-.-ι?ι the piston rings to the cooled wall of the cylinder so that detonation of the fuel is prevented, in split cycle engines the head of the power piston is deliberately maintained hot. As shown in Pig. it, the piston top 3δ 5 comprises a circular plate 59 of heat resistant material attached over insulating material iiO to the head of the piston 3<3» As the conduction of heat through the piston is not desired, the piston ring 38 can he made from plastic material. A conventional oil ring 1+1 is inserted 10 in the skirt or other convenient position on the piston. The compressor pistons often operate at such high speed that conventional air operated valves are inefficient ■ when used as inlet and outlet valves. A preferred construction for these valves is shown in Fig. 5 * in 15 which the valves are mechanically operated with the assistance of the air passing respectively into or out of the cylinder. This Figure 5 shows as an example the valves in the head of the high pressure stage ~ \ of the compressor. As the compressor remains cold, materials 20 of construction different from those employed in conventional internal combustion engines can be used. A circular inlet port i_2 formed in the head of cylinder 11 has an O-ring inserted in a downwardly tapering dovetail groove around its periphery on the face 25 of the head inside the cylinder. The inlet valve comprises a flat disc Iι3 covering the port 1+2 ana seating against the O-ring. A short stem kin- extends from a tightly fitting ball joint on the disc 1+3 outwardly of the cylinder 11+, and is formed as a part of the lever 1+5. 0 The lever k5 is pivoted intermediate its length about a rocker shaft k& ot which the central axis is coplanar with the seating surface of the disc 1+3. At its outer end 1+7, the lever 1+5 is rotated in a direction to close the port 1+2 by a helical spring 1+8. The end 1+7 ot the 5 lever is moved in opposition to the spring i+δ by a push δ . rod 1x9 actuated by a pivoted lever 50 bearing on a rotating cam 51 • A circular outlet port 52 formed in the head of the cylinder 1i+ has an C-ring inserted in an upwardly 5 tapering dovetailed groove around its periphery on the outside face of the cylinder head. The outlet valve comprises a flat disc 55 covering the port 52 and seating against the 0— ing. A short stem 51+ extends from, a tightly fitting ball joint on the disc 53 outwardly of 10 the cylinder 1i+, and is formed as a part of a lever 55♦ The lever 55 is pivoted intermediate its length about a rocker shaft 56 o which the axis is coplanar with the seating surface of the disc 5 * At its outer end 57, the lever 55 is rotated in a direction to close the port a. - ^ helical spring 58. The end 57 of the lever is moved in opposition tα the spring 5^> 07 tension in a cable 59 looped over the end. of a pivoted lever 60 bearing against a rotating cam o1 * Dovetail grooves ar -used to receive the 0-rings 20 because the air ,is ^ at such high pressure that, if plain, grooves were used, the air would penetrate beneath the 0-rings and lift them out of the grooves. The poppet valve 17 which admits high pressure air to the combustion chamber opens inwardly into the chamber, 25 and a spring closing it must have sufficient tension to hold it closed against the air pressing underneath the valve head in the direction to open it. If a conventional pus rod and tappet were used to operate the valve, the stress on the mechanism would be great 30 when the air pressure was relatively lew, such as when the engine is idling. An arrangement whereby the spring tension may be varied in conformity with the air pressure, and the stress on the operating mechanism thereby limited, ^ill new be described with reference to Fig. 6- The poppet valve 17 is held to its seat by a spring 6 in the normal manner. The bottom end of the spring 62 bea against a stop constituted by an internal flange 63 " formed on the open end of a tube 62+, which slides freely in a 5 valve spring compartment 65 formed on the outside of the cylinder 10. The other end of the tube 62+ is closed by a piston 66 of diameter greater than the seating diameter of face 67 of the valve 17» Valve 17 is actuated by a push rod 68 -)0 engaging an external rocker arm 69 attached to the end of a rocker shaft 70 supported by sealed bearings within the compartment 65. An internal rocker arm 71 is attached to the rocker shaft 70 within the compartment 65 and extends for a sufficient distance to enable it to engage the end 5 of. the stem o the valve 17 to open the valve when the push rod 68 is raised. As the pressure of the air entering behind the valve head 67 from the pipe 16 through a pert 72 increases the pressure inside the valve spring compartment 65 increases 0 y the same amount as the air pass.es,- to.it through a passage 73- The piston 66 is thereby lifted, taking the attached tube 62+ with it and compressing the spring 62. The tension which the spring 62 exerts on the valve to hold the head 67 against the seat accordingly increases 5 by the same amount, so that the valve operating gear is subjected to the same normal working strain at all times. The air bleed valve 23 is adjustable manually to permit a small amount of high pressure air from pipe 22 to pass to the air receiver 20 and build up its pressure 0 while the engine is running. _on return valve 21+ prevents the air from returning from the receiver 20. The volume of fuel delivered by fuel pump 37 is controlled in response to the variations of pressure of the air in the pipe 12 by the action of the air on a 5 spring loaded piston arrangement of known type. At all times while the engine is running, a supply cf compressed air of amount and pressure, suitable to keep the engine idling is available, either from the second stage of the compressor, or, if the pressure in the second stage is 5 too low, from the third stage of the compressor. Should the first stage of the compressor be completely unloaded, the second stage will inhale enough atmospheric air to maintain the engine idling after passing through the third stage. 0 The procedure when starting up the engine is as follows: The crankshaft of the engine 'is first turned by known means to a position at which the popp ' et valve 17, which admits high pressure air tα the firing cylinder 10, is open. The starter valve 21 is moved manually to the 5 "Start" position to allow compressed air from the receiver 20 to pass through pipes 19 and 12 into the cylinder 10. The piston 33 is thereby forced dov/n the cylinder 10 to rotate the crankshaft. A pipe 80 connects the pipe 30 through a valve 8 , 0 which operates in unison with the starter valve 21 , to a valve 82. A branch pipe 83 connects the pipe 80 to a valve 8 . The valves 82 and 82+ are normally closed. However, when actuated ay compressed air from, pipe 80, valve 82 opens thereby venting to atmosphere the high pressure 25 stage 1+ of the compressor 11, and valve 31A opens thereby venting to atmosphere the low pressure stage cf the compressor 11. In this way, the compressor is unloaded. A valve 85 opening to atmosphere fron the low pressure stage of the compressor 11 is opened oy • t Q compressed air directed to it through a pipe 36 which is connected to the pipe 30 through a valve 37 operated automatically by a speed governor 83. In a vehicle, it could also be operated by manual movement of the driver's accelerator. If the engine speed becomes excessive, the ■ -^ governor 38, or the accelerator, actuates the valve 37 to air supplied by the compressor 11 to the cylinder 10. In service which requires frequent acceleration and deceleration, for example in a road vehicle, the engine 5 according to this invention conserves energy by storing compressed air during deceleration instead of dissipating the energy as heat in a conventional braking system. This stored air can then be used in an ensuing period of acceleration. In order to store the compressed air, the 10 valve 15 is operated to direct the compressed air from the pipe 12 into pipe 18 and the air receiver 20, instead of into the firing cylinder 10 as in normal operation. The valve 15 is operated by a piston rod 8 attached a piston 90 moving in a cylinder 1 * A helical spring 92 J= urges the piston 90 to the left as shown in Pig. 1 , to maintain the pipes 12 and 1β in communication. T-Tien a brak pedal 93 is depressed, a lever 9 fixed to the pedal draws a rod 95 to the left against a helical spring 9β to operate a valve 97 to place a pipe 98 in communication through a ø- pipe 99 » a valve 00, and a pipe 101 with the pipe 30• The valve 100 is normally in the open position, so that compressed air flows through pipes 99 and 8 into the cylinder 91 to force the * piston 90 to the right, thereby cutting off the supply of compressed air to the pipe 1β 5 and directing it into the receiver 20. The engine accordingly ceases to perform work, and the inertia of the engine and vehicle is absorbed by the compressor 11 delivering air into the receiver 20 against the pressure of the air already there. 0 T»hen pressure is removed from the brake pedal 931 the spring 6 returns the rod 95 to the right, closing the pipe 99 and venting the pipe 8 to atmosphere through the outlet 102. The spring 92 then moves the piston 90 to the left, s that valve 15 is operated to direct compressed air from pip 5 12 to pipe 16, whereby the engine again supplies power to propel the vehicle. The valve 100 is operated by a rod 103 which moves to the left against a helical spring 1Ci_ when drawn by a lever 105 fixed to a clutch pedal 10β. The rod 03 is normally at the right hand limit of travel, and the spring 10l_ is unloaded, whereby the pipe 101 communicates with pipe 99. 7hen the clutch pedal 106 is depressed, for example when the vehicle is stopping, the valve 100 is moved so that pipe 101 is sealed, and pipe 99 is vented to atmosphere through an outlet 107. Thus, irrespective of the position of valve 97 j air pressure will be released from pipe 98 so that piston 90 will move to the left to operate valve 15 to direct compressed air from the pipe 12 through the pipe 16 to the cylinder 10 and maintain the engine running. Acceleration of the engine can be boosted by manually moving the valve 21 to the "Start" position, so that compressed air flows from the receiver 20 through the pipes 19* 12 and 16 to the cylinder 10 while the compressor 11 is unloaded. In this way, approximately 2G? * more power is o " delivered oy the engine without increasing fuel consumption for as long as the pressure of the air in the receiver 20 remains high enough. It is accordingly desirable to provide a pressure gauge on the receiver 20 for the guidance of the operator so that he will know when this method of increasing 5 acceleration is available. It is preferred, for maximum efficiency, to provide an expansion cylinder connected to the firing cylinder 10 with its associated piston driving the crankshaft in the manner disclosed in U.S. Patent _7o. it,136,561. 0 An engine may have a plurality αf firing cylinders of the above described construction connected to a common crankshaft.

Claims: Claims 1. A spark ignition internal combustion engine comprising a firing cylinder and a compression cylinder having reciprocating therein respectively a power piston and a compression piston connected to a common crankshaft, a 5 combustion chamber defined by the firing cylinder head, at least one recess containing valve heads and spark plug electrodes, and the crown of the moving power piston, characterised by means directing into the combustion chamber in advance of the spark as the power piston 0 approaches or reaches top dead centre a pilot charge composed of spark - ignitable fuel mixed with compressed air at a pressure below 2000 kPa, means producing a spark across the electrodes at or near top dead centre, and means directing into the combustion chamber after the 5 spark and while the piston is moving away from the cylinder head on the first part of the power stroke a second charge composed of fuel and air compressed to a pressure greater than 2000 k?a. 2. An engine according to claim 1 , characterised in that 0 deceleration is assisted by means diverting the compressed air supplied by the compression cylinder away from the firing cylinder, thereby reducing the pressure in the combustion chamber. 3. An engine according to claim 2, characterised in that 5 the diverted compressed air is directed into a compressed air receiver. h- An engine according to claim 1 , characterised in that the means directing compressed air into the combustion chamber comprise at least one poppet valve closed by a 0 helical compression spring bearing against a movable stop urged in the direction to close the valve by the pressure of the comτ.ressed air.

Inventors: WISHART JOHN D
Applicants: WISHART JOHN DONALD, WISHART JOHN D
Application year: 1981
Main classification: F02B3
IPC codes: F02B1, F02B3, F02B75