GB1194601A - Improvements in and relating to Internal Combustion Engines and Compressors - Google Patents

Abstract

1,194,601. Charging I.C engines, valve gear; driving gear; compressors. P.J. WALLS. June 7, 1967 [June 7, 1966], No.26268/67. Headings F1B and F1N. In double-acting I.C. engine or compressor each end of the cylinder has a detachable head 11 Fig. 1 carrying a smaller diameter cylindrical sleeve 10 extending towards the main cylinder, the main piston 5 has smaller diameter extensions slidable in the sleeves, the extensions have transfer chambers 8 with valve-controlled inlet and outlet ports 17, 20 whereby air compressed by the piston in the annular space 16 is further compressed in the sleeve 7 and eventually exhausted through the cylinder head. Fig. 1 I.C engine operation: Considering the left hand side of the engine with crank 30 rotating clockwise and piston 5 moving from right to left so that annular piston face 6 moves air (drawn in by a previous stroke) through ports 17 forcing the spring-loaded valve 18 open and thereby entering piston chamber 8. Valve 20 is forced open by the pressure difference between chamber 8 and combustion chamber 22 the air entering chamber 22 initial scavenges the remaining exhaust gases which pass out through port 23 under control of valve 24. Valve 24 and 20 are closed and continued piston movement compresses the air in chamber 22 until fuel injection and subsequent combustion take place. As piston 5 moves from left to right a fresh charge of air is drawn in through inlet 15 and chest 14 past spring-closed valve 13 into space 16, valve 18 being closed by spring 19 and the inertia effect caused by piston reversal. Valve 24 is opened towards the end of the exhaust stroke to complete the operating cycle. Valves 24 are operated from gudgeon pin 33 the ends of which slide in guides (35), Figs. 2 and 4 (not shown) formed in guide plates (35<SP>1</SP>) set in the sides of casing 1. The end of the gudgeon pin 33 moves in slotted cam levers 36, Fig. 3, having arms 36 connected to tie rods 26, Fig. 1, which move valves 24 through levers 25 pivoted to levers 27. Cam levers 36 are shaped so that rods 26 are moved alternately in the opposite direction to that of piston 5 so as to open the valve 24 away from which the piston is moving near the end of its stroke. Fig. 1a, compressor operation: The engine is run with the modified head 11 as shown in which the spring-loaded exhaust valve 24a opens outwardly at a predetermined pressure in space 22, the engine being driven externally. The engine may also be operated partly as on I.C. engine and partly as a compressor using one space 22 for combustion and the other space solely for compression. Fig. 11: In a modification auxiliary pistons 50, disposed co-axially on opposite sides of the main piston 5, are yoked together by cross beams 51 and links 59 connected with slippers 52 sliding in guides 53 and driven from crankshaft 30 through bell crank levers (32), Fig. 22 (not shown). The connection between the links and cross-beam have an adjustable eccentric in order to vary the clearance volume in space 22. The auxiliary pistons 50 move in synchronism with and in opposite directions to the main piston 5. Each valve 24 is carried by a spindle 62 which passes through a slot in cross piece 61 and the projecting ends, on each side of the piston 50, are connected by links 64, Fig. 15, secured to a spindle (66), Fig. 13 (not shown) journalled in a bore of the cross-beam 51 and is reciprocated by the latter. Cam rails 68, which are integral with crank members 65, co-operate with rollers 69 of arms 90 which are mounted on cylinder head 11 by means of eccentric pins 92 engaged in slots (91) in the arms 90. Pins 92 are carried by spindle 93 associated with adjustable pointer 94 and stationary disc 95 to provide for fine longitudinal movement of arms 90. Valves 24 are opened shortly before pistons 50 reach the outer end of their stroke by means of an inclined portion of the cam rail 68 which contacts roller 90. A crankshaft driven pump which may be omitted for spark ignition operation supplies fuel to the fuel injection aperture, or the pump may be used alternatively to pressurize the engine oil. The pump cylinders 39, Fig. 6 are carried by a circular casing 81 having a slotted engagement with pins 82 to permit limited rotary movement of casing 81 by movement of rod 83 connected to arm 84 thereby adjusting the timing of fuel injection. The engine may be reversed by adjustment of casing 81. Operation: When piston 5 is at the end of its stroke to the right as Fig. 11 pistons 50 are at the end of their stroke towards the left. Air from chest 14 has been admitted to space 16 past a valve 13, in the form of a ring resting on support 87. Valve 18 is closed and valves 20, 24 are open so that air entering the combustion space scavenges the exhaust gases. Ports 88 may be inclined to cause a swirling motion. As piston 5 commences moving to the left valve 13 closes, valve 18 opens and valves 20, 24 close after piston 5 moves a short distance. Fuel is injected into space 22 near the end of the compression stroke and combustion takes place as the pistons commence their return stroke. Valve 13 opens to allow a fresh air charge to be drawn into chest 14 and valve 18 closes. Towards the end of the return stroke valves 20, 24 open permitting the exhaust gases to be discharged through piston 50 assisted by the scavenging air. For petrol operation mixture is inducted into chest 14. The embodiment of Fig. 11 may be used as a compressor by replacing the auxiliary pistons by a piston (50<SP>1</SP>), Fig. 11a (not shown) incorporating a spring-loaded exhaust valve (24<SP>1</SP>). In all embodiments the pistons may drive the crankshaft through a crank, cam eccentric or pin and slot mechanism. The engine may be operated as a diesel engine, free-piston engine or petrol engine and the compression ratios adjusted by varying the thickness of valve ring 12. The smooth running of the engine may be improved by optional passages 29 in piston 5 which inter-connect chambers 28