Internal combustion engine

• US 5,285,752 A
• Filed: 04/23/1993
• Issued: 02/15/1994
• Est. Priority Date: 04/23/1993
• Status: Expired due to Fees

• Current Assignee: Single-Stroke Motors Incorporated
• Original Assignee: Single-Stroke Motors Incorporated
• Inventors: Villecco, Roger A., Frierson, Robert V., Reed, Jay L.
• Primary Examiner(s): Argenbright, Tony M.
• Assistant Examiner(s): Macy, M.
• Application Number:
  US08/053,249
• Time in Patent Office: 298 Days
• Field of Search: 123/61 R, 123/71 R, 123/62, 123/46 R, 123/196 AB, 123/41.33, 123/41.42, 123/197
• US Class Current: 123/61.00R
• CPC Class Codes: F01P 2003/006 the liquid being oil
• CPC Class Codes: F01P 9/00 Cooling having pertinent characteristics not provided for in, or of interest apart from, groups F01P1/00 - F01P7/00 profiting from waste heat of combustion-engine cooling F02G5/00
• CPC Class Codes: F02B 1/02 with positive ignition with non-timed positive ignition F02B9/06
• CPC Class Codes: F02B 1/04 with fuel-air mixture admission into cylinder
• CPC Class Codes: F02B 2075/025 two
• CPC Class Codes: F02B 29/0462 Liquid cooled heat exchangers
• CPC Class Codes: F02B 29/0481 Intake air cooling by means others than heat exchangers, e.g. by rotating drum regenerators, cooling by expansion or by electrical means
• CPC Class Codes: F02B 33/08 with the working-cylinder head arranged between working and pumping cylinders
• CPC Class Codes: F02B 33/10 with the pumping cylinder situated between working cylinder and crankcase, or with the pumping cylinder surrounding working cylinder
• CPC Class Codes: F02B 75/002 Double acting engines
• CPC Class Codes: F02B 75/065 with double connecting rods or crankshafts
• CPC Class Codes: F02B 75/16 Engines characterised by number of cylinders, e.g. single-cylinder engines F02B75/26 takes precedence
• CPC Class Codes: Y02T 10/12 Improving ICE efficiencies

Abstract

A single piston internal combustion engine is described that produces two power impulses per revolution of the crankshaft, precise mechanical balance, zero side thrust upon the piston, and purified exhaust gas. The lubrication oil is isolated from contamination by blowby and fuel dilution. Total engine cooling is obtained from the lubrication oil. The engine is free from shock loads as it is cushioned by continuously compressing gas in preparation for the next combustion event. The engine is uniflow-scavenged utilizing piston pumps whose fresh air intake is controlled by rotary valves. The piston pumps possess compact aftercoolers used in combination with supercharging. The exhaust header assists in silencing the engine and removes fluctuations in exhaust pressure. A computer-aided specialized mechanical balance methodology is disclosed that obtains counterbalance weights to optimally reduce engine shaking forces. The engine is suitable for operating on alternative fuels such as liquified natural gas, and alcohol.

Claims

1. A two-stroke cycle internal combustion engine comprising:

(a) first, second, and third axially elongated cylinders disposed in axial alignment;

(b) a piston assembly possessing first, second, and third pistons disposed in axial alignment, spaced axially apart, and fastened upon first and second hollow rods;

(c) said first and second hollow rods joined together by a hollow nipple within the interior of said second piston, thereby forming a sealed toric cavity within said second piston;

(d) said piston assembly disposed to reciprocate in the axial direction within said axially aligned first, second, and third cylinders, wherein said first, second, and third pistons possess top and bottom dead center positions within said cylinders;

(e) said second cylinder, closed at one end by a first head and closed at the remaining end by a second head, in which said second piston possesses a double crown, thereby forming separate first and second combustion chambers;

(f) said second cylinder possessing a multiplicity of openings about the equator of said second cylinder, thereby forming exhaust gas ports that are fully open when said second piston is in either said dead center position;

(g) the reciprocation is driven by alternating deflagrations within said separate combustion chambers of said second cylinder;

(h) said first cylinder joined and separated from said second cylinder by said first head, wherein said first head possesses a first gland to guide said first rod during said reciprocation;

(i) said third cylinder joined and separated from said second cylinder by said second head, wherein said second head possesses a second gland to guide said second rod during said reciprocation;

(j) said first and third cylinders and first and third pistons form first and second scavenging pumps, each possessing a rotary disc valve, and fresh air intake ducts, for phase controlled fresh air intake means;

(k) means for removing the heat of compression of the compressed fresh air within said scavenging pumps;

(l) phase controlled means for scavenging and releasing the spent exhaust gas from said combustion chambers into a toric exhaust gas header that surrounds said exhaust gas ports;

(m) means to extract heat from said engine by utilizing the oil from the engine'"'"'s crankcase as the cooling medium;

(n) means to convert said reciprocation into a rotary motion;

(o) means to utilize said rotary motion to drive idler gears; and

(p) means to lessen the crankcase pressure pulsations resulting from said reciprocation of said first and second scavenger pumps.

2. The engine as recited in claim 1, wherein said piston assembly includes:

a proximal end and a distal end;

said first piston is located at said distal end and joined to said second piston by said first hollow rod;

said third piston is located at said proximal end and joined to said second piston by said second hollow rod;

said first and third pistons possess gas sealing rings; and

said second piston possesses pinned gas sealing rings.

3. The engine as recited in claim 1, wherein said second scavenging pump penetrates and rigidly joins said crankcase.

4. The engine as recited in claim 1, wherein said rotary disc valves are mutilated thin circular discs, and reside transversely between said first scavenger pump and said first head, and between said second scavenger pump and said second head, and the axis of disc rotation is coincident with said axial alignment, and said discs possess means to rotate at the engine frequency, thereby opening and closing said fresh air intake ducts of said first scavenger pump and said second scavenger pump to obtain said phase controlled fresh air intake means.

5. The engine as recited in claim 1, wherein said means for removing the heat of compression includes:

heat exchangers contained within the clearance volumes of said scavenger pumps;

said heat exchangers communicate with a pump and a liquid to air radiator to form a closed loop heat transfer system; and

a circulating heat transfer fluid within said closed loop heat transfer system, thereby removing said heat of compression of said compressed fresh air.

6. The engine as recited in claim 1, wherein said scavenging is obtained by the phase controlled transfer of the said compressed fresh air into said first and second combustion chambers from said first and second scavenging pumps when said exhaust gas ports are opened by said second piston.

7. The engine as recited in claim 6, wherein said phase controlled transfer of said compressed fresh air is obtained by flutelike slots in said hollow rods adjacent to said first and third pistons, thereby allowing the phased communication of said first combustion chamber with said first scavenging pump, and said second combustion chamber with said second scavenging pump, through said first and second glands.

8. The engine as recited in claim 1, wherein said heat extraction means includes:

a positive displacement oil pump, possessing a pressure relief valve, to force oil from said crankcase through a filter and oil cooler;

said oil cooler possesses a ducted electric fan controlled by a thermoswitch to draw air through said oil cooler when required;

said oil cooler feeds said oil into said first hollow rod of said piston assembly during said reciprocation through a stationary thin wall tube axially aligned and penetrating into the interior of said first hollow rod;

said cool oil flows rectilinearly through said piston assembly and returns to said crankcase by said second hollow rod, thereby maintaining mechanical balance; and

said toric cavity within said second piston contains a small amount of heat transfer fluid.

9. The engine as recited in claim 1, wherein said converting means includes a configuration comprising:

two crankshafts whose single crankpins are phased synchronized by gearing to possess mirror symmetry during their rotation;

said crankshafts possess equal crank arm lengths;

the axis of said mirror symmetry lies on said axis of alignment;

said idler gears engage said gearing and preserve said mirror symmetry and rotate at twice the frequency of said crankshaft rotation;

said idler gears mesh, thereby reducing the stress upon the teeth of said synchronizing gearing;

said second scavenging piston possesses two piston pins whose midpoint of separation lies on said axis of alignment;

each said crankpin attaches to each said piston pin by a connecting rod;

said configuration causing the engine'"'"'s center of mass oscillation along the direction of said axis of alignment to be analytically described by a Fourier cosine series whose argument is the crankshaft angle, plus a sine term whose argument is said crankshaft angle, and plus a sine term whose argument is twice said crankshaft angle; and

means for balancing the reciprocating mass of said engine utilizing counterbalance weights installed upon said gearing and idler gears, thereby optimally reducing the shaking forces.

10. The engine as recited in claim 9, wherein said balancing means includes a computer aided method to obtain the masses and locations of said counterbalance weights upon said gearing and idler gears to eliminate the coefficients of the first and second terms of said Fourier cosine series, as well as the coefficient of both of said sine terms, thereby diminishing said center of mass oscillation.

11. The engine as recited in claim 4, wherein said means to rotate at engine frequency includes:

each said rotary disc valve engages by spline fit the driven gear of a set of bevel gears;

the gear ratio of said bevel gears is 1 to 2, wherein the driven gear obtains one-half the rotational frequency of the drive gear;

rotary power take off is obtained from said idler gears; and

said rotary power from said idler gears is transmitted to each said drive gear by individual flexible shaft drives.

12. The engine recited in claim 1, wherein said means to lessen the crankcase pressure pulsations includes:

a breathing pipe of substantial cross sectional area, possessing a proximal end and a distal end;

the proximal end of said breathing pipe communicates with a swept volume of said second scavenging pump at the crankcase side of said second scavenging pump;

the distal end of said breathing pipe communicates with a swept volume of said first scavenging pump at the distal end of said first scavenging pump; and

said breathing pipe is oriented to return oil mist and droplets to said crankcase by the force of gravity.