WO1994019589A1

WO1994019589A1 - A power output boosting engine piston

Info

Publication number: WO1994019589A1
Application number: PCT/KR1994/000013
Authority: WO
Inventors: Un Kil Paek
Original assignee: Un Kil Paek
Priority date: 1993-02-23
Filing date: 1994-02-22
Publication date: 1994-09-01

Abstract

An engine piston for exerting maximum gas pressure with minimum expansion force comprises: a small, oval piston (10), a sleeve (30) separately movable over the piston within a piston cylinder (80), and two automatic clutches having each a spring-loaded latch (40) mounted in the sleeve, locking the piston normally, and a servo cam key (60) mounted in the piston for unlocking the piston in expansion strokes and locking the piston cylinder (80) momentarily so as to provide: the piston combined by the sleeve in compression strokes for reciprocating together to compress much gas; the piston detached from the sleeve in expansion strokes for dashing alone through a sleeve cylinder (39) to exert stronger pressure; and the piston re-combined in exhaust strokes for reciprocating together to exhaust the gas. The latch (40) has a sliding bar (49) with an internal bolt (50) to lock the piston normally and an external bolt (54) to lock the piston cylinder (80). The servo cam key has a piston rod (67) and mouth pieces (61) to unlock the latch (40).

Description

A POWER OUTPUT BOOSTINQ ENQINE PISTON

Technical Field

This invention relates to an internal combustion engine of an automobile, especially to a piston mechanism so improved as to generate maximum expansion pressure (engine power output) with minimum expansion force, thereby saving fuel by over fifty percent over the prior art and emitting less polluted gas by that much. Background Art A conventional piston/connecting rod power transmission mechanism consisted of a piston with a pistonhead at one end and a skirt at the other end and a pistonpin in the center, of a connecting rod with a small end thereof mounting on the pistonpin at one end and with a big end mounting on the crankpin of a crankshaft at the other end, and of a piston cylinder so as for the piston to recip¬ rocate therethrough with expansion forces for the purpose of exerting greater power outputs and transmitting them to the crankpin to rotate the crankshaft. The pistonhead of this piston mechanism, however, had such an inseparable, round surface that four strokes - suction, compression, expansion, and exhaust - were all carried out by one while surface area.

This type of simple piston arrangement was regarded as unsatisfactory for generating maximum engine power outputs with minimum expansion forces, because unlike the air hose hole at the bottom of an air pump being reasonably very small for exerting a stronger air pressure, compared with the cylinder of the air pump, which is substantially very

SUBSTITUTESHEET big for sucking and compressing much air in the cylinder, the cylinder that the expanded gas would flow out through, pushing the pistonhead for exerting a strong expansion pressure, was the same one that the pistonhead was recip- rocating through for sucking and compressing the mixed gas, thus causing' the expanded gas to flow out at' a time in a volume too large to generate a stronger, longer pressure. This simple arrangement _r therefore, required much more frequent, stronger expansion force to maintain the same stronger, longer engine power output, resulting in consump_¬ tion of fuel in a larger quantity and emission of polluted gas as much and in quick wearing of and damages to the engine parts due to the overheat and the overload. Disclosure of Invention This invention came into conception in view of the above problems and from the careful study of the operation of an air pu p. Its object is to provide a mass compression piston means with a large pistonhead applicable in suction and compression strokes for performing suctions and comp- ressions of gas as much as possible; another object is to provide a pressure boosting piston means with only a small, central portion of the pistonhead being acted on and pushed down separately by expansion forces in expansion strokes for performing dashings through a small cylinder to exert a stronger expansion pressure in accordance with the principle of hydraulic pressure and the third object is to provide a mass exhaust piston means with the whole piston¬ head applicable in exhaust strokes for exhausting all the expanded gas. To this end this power output boosting engine piston comprises, in place of a conventional engine piston with a pistonehad at one end, a skirt at the other end, and a pistonpin in the center being mounted on by the small end of a connecting rod in a piston cylinder, a small, oval piston(10) in the center, a sleeve (30) separately movable over the piston within a piston cylinder (80) , and an automatic clutch (40, 60) being partly mounted in the piston and partly in the sleeve for carrying out the power output boosting performance; ■ wherein the improvement comprises: the small piston (10) being formed with an oval piston¬ head (11) being less than half the pistonhead of a conven¬ tional piston: small for exerting maximum expansion pressure with minimum expansion force, oval in shape for allowing the sleeve (30) to house a latch set (40) of the automatic clutch in either thick side of the sleeve (30); the sleeve (30) being formed in a pipe with an internal¬ ly oval cylinder (39) for providing room in either thick side thereof for housing the latch set (40) each, and being disposed over the small piston (10) for reciprocating independently of the small piston (10); the automatic clutches each containing the contract coil spring-loaded latch set (40) and a servo cam coil spring-loaded key set (60) each for causing the sleeve(30) to clutch at the small piston(10) by the latch spring means in suctio and compression strokes, to de-clutch^*from the piston(10) and to clutch at the piston cylinder(80) omen- taraly by the servo cam means in the last stage of comp¬ ression strokes and in the early stage of expansion strokes, and to de-clutch from the piston cylinder(80) soon there- after so as for the sleeve(30) to follow the small piston (10) all the way down to the bottom dead center to avoid break-off and to clutch at the small piston(10) by the latch spring means in exhaust strokes; and the small piston(lθ) being connected to the small end of a connecting- rod,^, with the servo cam spring-loaded key set(60) mounted in and attached to the piston(10); the sleeve(30) being reciprocatably disposed over the piston (10) with the latch set(40) mounted in and attached to the sleeve(30), locking the piston(10) normally; the small piston(10) and the sleeve(30) thus set up being inserted in the conventional piston cylinder(80) for proper opera¬ tion so as to provide: mass compression means of the small piston(lθ) being combined by the sleeve(30) via the auto- matic clutch in suction and compression strokes for recip¬ rocating together with the sleeve(30) so as to suck and compress gas as much as possible; gas pressure boosting means of the small piston(10) being detached from the sleeve(30) and simultaneously the sleeve(30) being stuck to the piston cylinder(δθ) via the clutch in expansion strokes for dashing down independently through the sleeve cylinder(39) so as for the small piston(10) to exert much stronger pressure; and exhaust means of the small piston (10) being re-combined by the sleeve(30) via the clutch in exhaust strokes for reciprocating together so as to exhaust the gas as- much as possible. Brief Description of Drawings

Pig 1 shows a top-sectional view of a power output boosting piston with a small, oval piston, a sleeve, and two clutches according to the invention. Fig 2 shows a side-sectional view of such a piston, a sleeve, and two clutches positioned at the top dead center at the start of suction stroke.

Fig 3 shows a perspective view of such small, oval piston 5 and an exploded view of a servo cam drive member.

Fig 4 shows a perspective view of a servo cam driven member. Fig 5 shows a perspective view of a sleeve with a latch case housing.

Fig 6 shows an exploded view of a latch set. 10 Drawing Reference Numerals

10 small, oval piston 11 pistonhead

12 servo cam drive member housing

13 servo pistonrod bore 14 spring housing

15 oil passage 16 servo piston cylinder

1 17 cylinder cap hole 18 cam driven member housing

19 internal bolt groove 20 internal bolt channel

21 shallow base 22 deeper base

23 plain bearing 24 tap bolt

25 pistonpin boss 26 piston skirt

20 27 buffer spring housing 28 buffer spring

29 screw 30 sleeve

31 latch case housing 32 internal bolt bore bosshole

33 cover housing 34 tap bolt hole

35 ring groove(external) 36 oil groove (external)

25 37 ring groove(internal) 38 oil groove (internal)

39 sleeve cylinder 40 latch set

41 latch case 42 internal bolt bore boss

43 tap bolt hole 44 washer

45 tap bolt 46 cover

3047 external bolt bore 48 tap bolt hole 49 sliding bar 50 internal bolt

51 internal bolt point 52 roller 53 sliding bar block 54 external bolt 55 external bolt point 56 spring block 5 57 spring loading section 53 contract coil spring 59_" piston, skirt groove. 60 , servo cam key set 61 close-open mouth piece 62 angled corner

63 indented, curved sideface

64 tension spring housing 65 tension spring peg 10 66 tension spring 67 servo pistonrod

68 V-shaped point 69 square sliding section 70 servo piston section 71 servo piston ring groove 72 servo piston ring 73 contract coil spring 74 cylinder cap 80 piston cylinder

15 81 sleeve block 82 external bolt groove

83 external bolt channel Best Mode for Carrying Out the invention

An improved engine piston for exerting maximum engine power outputs with minimum expansion forces comprises, in

20 place of a conventional engine piston with a pistonhead at one end, skirt at the other end, and a pistonpin in the center being mounted on by the small end of a connecting rod in a piston cylinder: a small, oval piston(10) in the center, a sleeve(30) separately movable over the piston

25 (10) within the piston cylinder(δθ) , and an automatic clutch(40, 60) mounted partly in the small pisto (10) and partly in the sleeve(30) for pressure-boosting performance in expansion strokes.

The improvement thereof comprises:

30 The small piston(lθ), as shown in Figs 1, 2, and 3, is formed with an oval pistonhead(11 ) being less than half the pistonhead of a conventional piston: small for exerting maximum expansion pressure with minimum expansion force by blowing out expanded gases through a sleeve cylinder(39) , oval in shape for allowing the sleeve(30) to house a latch set(40) of the .automatic clutch in. either side of -the sleeve(30). The small piston(lθ) has pistonpin bosses(25) on either diarnetically wider side in the center for connect¬ ing the piston(10) to the small end of the connecting rod and has a partially projecting piston skirt(26) being extended as wide as the sleeve(30) on either diarnetically wider side for facilitating stable, separate reciprocation of the small piston(10) through the piston cylinder(BO) and a curved, square buffer spring housmg(27) being formed on the upper surface for holding a buffer expandable spring (28) by screw (29) for easing impacts of the sleeve(30) on the piston skirt(26) at the start of exhaust strokes, and the buffer expandable spring(28) being elastic enough to ease the impacts, The sleeve(30), as shown in Figs 1, 2, and 5, is formed in a pipe with the internally oval sleeve cylinder(39) for providing room in either thick side thereof for housing the latch set(40) each, and disposed over the small piston(10) for reciprocating independently of the small piston(10). The sleeve(30) has a ring groove(37) and oil groove(38) formed on the internally oval cylinder(39) like a conven¬ tional ring groove(35) and oil grooves(36) on the external surface and a square piston skirt groove(59) being formed each at the bottom thereof on either side for receiving the projecting piston skirt(26). The automatic clutch, as shown in Figs 1, 2, 3, 4, and 6, comprises the latch set(40) being each mounted in either thick side of the sleeve(30) at a lower section of the sleeve(30) for locking the small piston( θ) normally by latch spring means but unlocking the piston(lθ) and locking the piston cylind.er(80) as. lo g, as possible in expansion,, strokes so as to allow the piston(lθ) to dash down alone for exerting stronger, longer pressure, and a servo cam key set(60) being mounted in the small piston(lθ) for unlocking the latch set(40) in expansion strokes by servo cam means, thus releasing the small piston(10) and enabl¬ ing the latch εet(40) to lock the piston cylinder(80) momentarily so as to allow the small piston(10) to dash down ahead of the sleeve(30) and to join together in exhaust strokes;

The latch set(40) contains a latch case(41), a cover (46), a sliding bar(49), a contract coil spring(58), washer (44), tap bolts(45), a latch case housing(3l), an internal bolt groove(19), an internal bolt channel(20), a sleeve block(8l), an external bolt groove(82), and an external bolt channel(83);

The square latch case(4l) has a square internal bolt bore boss(42) being formed on one side surface and tap bolt holes(43) on the sectional walls of the opposite side surface. The square, curved cover(46) has a square, thick, external bolt bore(47) in the center thereof and tap bolt holes(48) at spaced locations for attaching the .cover(46) to the latch case(41) and to the circumferential surface of the sleeve(30) through tap bolt holes(43, 48) with the washers(44) and the tap bolts(45). The elongated sliding bar(49) has a square, internal bolt(50) with a U-shaped point(5l) at one end for getting in and out of the internal bolt groove(19) of the small piston (10), a square, external bolt(54) with a U-shaped point(55) at the other end for getting in and out of the external bolt groove(82), a sliding-bar block(53) , a spring block(56), and a spring loading section(57) in between. The contract coil spring (58), with another coil spring(73), is strong enough to yield to the highest compression force in the last stage of compression strokes and to the expansion force in the early stage of expansion strokes. The square latch case housing (31) comprising a square internal bolt bore boss hole(32), an indented cover housing(33), and tap bolt holes(34) is each formed at a lower section of the sleeve(30) for keep- ing the external bolt(54) locked in the piston cylinder(80) longer at all possible while the piston(lθ) is dashing down alone to exert strong pressures.

The internal bolt groove(19) is formed each in square shape in the lower portion of the piston(lθ) on either side for the internal bolt(50) to lock in in suction and compre¬ ssion strokes and exhaust strokes. The internal bolt chan- nel(20) with a shallow base(2l) below and a deeper base(22) above half the length of the channel(20) is formed in either side from the internal bolt groove(l9) close to the pistonhead(11 ) for the internal bolt(50) to move to and to slide on the shallow base(21) by the contract coil spring(58), keeping the external bolt(54) locked' in the external bolt groove(82) of the piston cylinder(8θ) as long as possible so as to allow all the expanded gas to flow through the narrow sleeve cylinder(39), pushing the small piston(lθ), before the internal bolt(50) slides onto the deeper base(22) to allow the external bolt(54) to get out of the external bolt groove(82), thus permitting the sleeve(30) to follow the small piston(10) to the bottom dead center smoothly.

Tke ring-shaped sleeve block(8l) projects from- the- piston cylinder(80) at the top dead center for preventing the sleeve(30) from further upward movement. The external bolt groove(82) is formed in .square shape in either side of the piston cylinder(80) at the top dead center so as for the external bolt(54) to lock in a little while before and in the early stage of the expansion strokes. The external bolt channel(83) is formed right below the external bolt groove(82) on either side and below the level of the small pistonhea (11 ) being at the bottom dead center in order not to allow gas to flow therein but to allow the external bolt(54) to pass through freely while the internal bolt(50) is sliding back from the deeper base(22), the shallow base(2l) and into the internal bolt groove(l9) in exhaust strokes.

The sliding bar(49) is disposed in the latch base(4l) with the internal bolt(50) projecting through the internal bolt bore boss hole(32); the contract coil spring(58) is loaded on the spring loading section(57) of the external bolt(54); the cover(46) is put over the latch case(4l), depressing the spring(58) and getting the external bolt(54) in the external bolt bore(47), and joined firmly to the latch case(4l) through the tap bolt holes(43) by the wash- ers(44) and the tap bolts(45); the latch case(41 ) thus set up is mounted in the latch case housing(3l) of the sleeve (30) with the internal bolt(50) projecting through the internal bolt bore boss hole(32) and joined to the sleeve (30) with the washers(44) and the tap bolts(45) for proper operation of the latch set(40). The servo cam key set(60) contains a cam drive member of a contract coil spring-loaded pistonrod(67) being mounted in the central, upper portion of the piston(10) for recipro_¬ cating downward by gas pressure means and upward by spring means and a cam driven member of a tension spring loaded, close-open mouth pieces(6l) being mounted in the lower portion of^' the piston(lθ) between the internal bolt grooves' (19) on either side thereof for being pushed open sidewise by the cam drive member(67) so as for each mouth piece(61) to push the internal bolt(50) out of the internal bolt groove(l9) to the level of the shallow base(21 ) of the internal bolt channel(20) in the last stage of compression strokes and the early stage of expansion strokes.

The cam drive member contains the pistonrod(67) , a contract coil spring(73), a cylinder cap(74), and a servo cam drive member housing(12). The pistonrod(67) has a square, V-shaped point(68) at the lower end for sliding downward between the indented, curved sidefaces(63) of the mouth pieces(6l) for perfect, easy opening of the mouth pieces(6l); a square sliding section(69); a servo piston section(70) with ring groove(7l) and ring(72). The cont¬ ract coil spring(73), with the coil spring(58), is strong enough to yield to the highest compression force in the last stage of compression strokes and in the expansion strokes. The cylinder cap(74) has an externally threaded surface for joining it firmly to the small pistonhead(11 ) and a multi-faced hole therein for allowing the gas to flow through and for use in screw driving of the cylinder cap(74). The servo cam drive member housing(l2) has an internally threaded cylinder cap hole(17) at the pistonhead (11), a servo piston cylinder(16) being so long that the pistonrod reciprocation may open the¹ mouth pieces'(6l ) to the level of the shallow base(2l), an oil passage(15) being formed each from the deeper base(22) to the servo piston cylinder(l6) , a round spring housing(14), and a square servo pistonrod bore(13) above the central portion of a servo cam driven member housιng(lδ). The contract coil sprmg(73) is placed in the servo cam drive member housing (12), the pistonrod(67) is put next therein and the cylinder cap(74) is screw driven into the cylinder cap hole(l7), depressing the pistonrod(67) so as for the V-shaped point (68) to rest between the indented, curved sidefaces(63) in preparation for sliding down between the mouth pieces (61) to open wide in expansion strokes.

The servo cam driven member contains a pair of the close-open mouth pieces(6l) and of tension springs(66), and a servo cam driven member housing(18). Each mouth piece (61) has a contact sideface with angled corners(62) and an indented, curved sideface(63) in the center for allowing the V-shaped point(68) of the pistonrod(67) to slide against the curved sideface(63) to open the mouth pieces (61) sidewise easily and a tension spring housing(64) and a tension spring peg(65) being formed on either side there¬ of. The tension springs(66) are just strong enough to bring the twin mouth pieces together quickly. The servocam driven member housing(lδ) is formed in square shape between the internal bolt grooves(19). The twin mouth pieces(6l) are put together, the tension springs(66) are loaded in the spring housing(64) in either side and hooked on either spring peg(65) strained. The mouth pieces(61) thus set up are mounted in the servo cam driven member housing(18) with the V-shaped point(68) of the pistonrod(67) resting between the indented, curved sidefaces(63).

The cam driven member and the cam drive member of the servo cam key set(60) are mounted in order in the small piston(lθ) as above, the sleeve(30) is disposed over the small piston(10), and then the latch set(40) is mounted in the sleeve(30) locking in the internal bolt groove(19) and joined to the sleeve(30) in preparation for perfect performance. In addition to the above assembly a plain bearing(23) may each be attached to the shallow base(2l) through the deeper base(22) of the internal bolt channel(20) in either side of the piston(10) by tap bolts(24) and a roller(52) may also each be installed on the internal bolt points(5l) for secure, smooth slidings of the internal bolts(50). The Advantage of Invention

For better understanding of this invention something about expansion force in an air-tight cylinder and its related formula for its effect on a pistonhead should be discussed before the advantages of this invention are enumerated.

An expansion force in an air-tight piston cylinder is a force to enlarge the limited capacity of the cylinder as quickly as possible by blowing out the piston therein, as the gaa compressed by a piston in an air-tight cylinder gets ignited, burning rapidly, and becoming bulky many times. So, should a piston cylinder be small in diameter, an excessively bulky gas in the cylinder has to leave the limited cylinder in a certain large volume at a given time by pushing out the small pistonhead at a much stronger, more rapid speed, thus increasing the gas pressure. The explosive force of the gas to push out the piston from the cylinder is so called heat energy. The heat energy is divided by a pistonhead area to produce a gas pressure or engine power output. The smaller the pistonhead, the more powerful the gas pressure is. This reasoning is supported by a book entitled "Automotive Transmissions and Power Trains" by vάlliam H. Crouse, McGraw-Hill Book Co., in its paragraph 7.4 (Transmitting Pressure by Liquid), Chapter 7 (Torque converters) (page 129).

Suppose that P (force) represents an expansion force or heat energy; A, a conventional pistonhead area; P, a pres¬ sure applied on the pistonhead area; a , a small piston¬ head area of this invention; and that p represents a pres- sure on the small pistonhead area. Then the related formula for the gas or hydraulic pressure is as follows:

F/A (F divided by A) = P. F/a = p.

F = A x P = a x p. p = P x A/a.

Suppose, for example, that the ratio between the con- ventional pistonhead area and that of this invention is 2 to 1; then the calculation will be: p = P x A/a = P x 2/1 = 2P or 200 of P.

That is, the small pistonhead will exert twice as much pressure as the conventional one iid when the same amount of gasoline is used. Accoraingly, an improved pistonhead according to this invention will preferably be made as small as possible to exert much pressure, unless it does any harm to the piston cylinder, the sleeve, the piston, and to the clutch. This invention, therefore, enables engine mechanism to operate with much less fuel for exert_¬ ing j st' enough engine power- outputs. The objects and the advantages of this invention are:

To provide an engine piston for performing efficient reciprocations with minimum energy(minimum expansion force) required in rotating a crankshaft, thereby saving fossile fuel as much as possible (by over fifty percent over the prior art) and reducing polluted gas emissions as much or more from a reasoned statement that the gas mixed with less gasoline will burn perfectly; to provide an engine piston which allows a car to run efficiently with a four-cylinder engine in place of a six-cylinder engine, resulting in dispensing with two cylinders and lightening the car weight, thus saving further energy and emitting less polluted gas: to provide an engine piston which keeps the engine parts from quick wearing caused by overheat and overload and keeps the engine from excessive vibrations and noises; to provide an engine piston which allows drivers not to depress accelator pedals so hard as before; to provide an engine piston for performing stronger reciprocations with stronger expansion forces to meet heavy duty carriage.

Further objects and advantages of this invention will become apparent from a consideration of drawings and the description of it.

Thus, the reader will see that this invention will provide a highly reliable, economical engine piston for perforraing appropriate reciprocations as necessary to compress much gas in suction and compression strokes, to exert maximum pressures with minimum expansion forces in expansion strokes, and to exhaust the expanded gas in exhaust strokes in accordance with the principle of the hydraulic pressure or air pressure.

Though the above description contains only one speci¬ ficity, it should not be construed as limitations in the scope of the invention, but rather as an exemplification of preferred embodiments thereof. Those skilled in the art will envision other possible variations within its scope. For example, skilled artisans, in place of the automatic clutch described above , will be able to utilize a different type latch set with one latch bolt mounted in either side of the small piston locking a sleeve by spring means norm¬ ally, and a servo cam key bolt/external latch bolt set mounted in either side of the sleeve so as for the servo key bolt to unlock the latch bolt and for the external bolt to lock the piston cylinder in expansion strokes and to return to the original position as the expandedgas weakens. They can also use an automatic clutch similar to a break shoes mechanism mounted around the sleeve for clutching at the small piston by spring means normally and declutching from the small piston and clutching at the piston cylinder momentarily by a servo means in expansion strokes and returning to the original position by the spring means, as the expansion pressure becomes weakened.

Accordingly the reader is requested to determine the scope of the invention by the appended claims and their legal equivalents, and not by the embodiment given above.

Claims

Claims :

Claim 1. A power output boosting engine piston for exert_¬ ing maximum expansion pressures with minimum expansion forces comprising, in place of a conventional piston, a small, oval piston(10) in the center, a sleeve(30) separa_¬ tely movable over said piston(10) within a, piston cylinder.. (80), and an automatic clutch(40, 60) being mounted partly in said piston(10) and partly in said sleeve(30) for proper clutch operation; . wherein the improvement comprises: said small piston(lθ) being formed with an oval piston- head(H) being less than half the pistonhead of said con_¬ ventional piston: said small piston(lO) being small for exerting maximum expansion pressure with minimum expansion force and oval in shape for allowing said sleeve(30) to house said automatic clutch means(40, 60) partly in either thick side of said sleeve(30); said sleeve(30) being formed in a pipe with an inter¬ nally oval cylinder(39) for providing room in either thick side thereof for housing said automatic clutch means(40,60) partly, and being disposed over said small piston(10) for reciprocating independently of said small piston(lθ); said automatic clutch means(40, 60) for causing said sleeve(30) to clutch at said small piston(10) in suction and compression strokes, to de-clutch from said piston(lθ) and to clutch at said piston cylinde (80) in the last, stage of compression strokes and in the early stage of expansion strokes, to de-clutch from said piston cylinder(80) soon thereafter so as for said sleeve(30) to follow said small piston(10) all the way down to the bottom dead center, and to clutch at said piston(10) in exhaust strokes; and said small piston(lθ) being connected to a connecting rod, with said automatic clutch means(40, 60) mounted partly in and attached to said piston(lθ); said sleeve(30) being reciprocatably disposed over said piston(10) with said automatic clutch means(40, 60) mounted partly in and attached to said sleeve(30) locking said piston(lθ) normally; said piston(10) and said sleeve(30) thus set up being inserted in said conventional piston cylinder(SO) for proper operation so as to provide: mass compression means of said small piston(10) being combined by said sleeve(30) via said automatic clutch in suction and compression strokes for reciprocating together so as to suck and compress mixed gas as much as possible; gas pressure boosting means of said piston(lθ) being detached from said sleeve(30) and simultaneously said sleeve(30) being stuck to said piston cylinder(δθ) via said clutch in expansion strokes for dashing down inde¬ pendently through said sleeve cylinder(39) so as for said piston(10) to exert much stronger pressure; and exhaust means of said piston(10) being re-combined by said sleeve(30) via said clutch in exhaust strokes for reciprocating together so as to exhaust said gas. _Claim

2. The power output boosting engine piston of claim 1 wherein said small piston(10) comprises a partially proj¬ ecting skirt(26) being extended s wide as said sleeve(30) on either diarnetically wider side for facilitating secure, stable, independent reciprocations of said small piston (10) through said piston cylinder(80) all the way down to the bottom dead center, apart from said sleeve(30), a square, curved buffer spring housing(27) being formed on the upper surface thereof for holding a buffer expandable spnng(28) by a screw(29), and said buffer sprmg(28) being elastic enough to ease impacts of said sleeve(30) upon said piston skirt(26) at the start of exhaust strokes; said buffer sprιng(28) being attached to said spring housing(27) by said screw(29) in either side.

Claim 3. The power output boosting engine piston of claim 1 wherein said sleeve(30) comprises a ring groove(37) and an oil groove(38) being formed on said internally oval cylmder(39) like a conventional ring groove(35) and oil grooves(36) on the external surface and a square, curved piston skirt groove(59) being formed each at the bottom thereof on either side for receiving said projecting piston skirt(26).

Claim 4. The power output boosting engine piston of claim 1 wherein said automatic clutch means comprises a latch set(40) being each mounted in either thick side of said sleeve(30) at a lower section of said sleeve(30) for caus- ing said latch set(40) to lock said piston(10) normally so as to allow both said piston(lθ) and said sleeve(30) to reciprocate together but to unlock said piston(10) and lock said piston cylinder(80) as long as possible in exp¬ ansion strokes so as to allow said piston(10) to dash alone through said sleeve cylinder(39) for providing stronger pressure, and a servo cam key set(60) being mounted in said piston(10) for causing said key set(60) to unlock said latch set(40) in expansion strokes, thus releasing said piston(10) and enabling said latch set(40) to lock said piston cylinder(SO) momentarily so as to allow said piston(lθ) to dash down ahead of said sleeve(30) and to join together in exhaust strokes.

Claim 5. The power output boosting engine piston of claim 4 wherein said latch set(40) comprises a latch case(4l), a cover(46), a sliding bar(49), a contract coil spring

( 8),. washers(44) , tap bolts(45), a latch case- housing(31) , an internal bolt groove(19), an internal bolt channel(20), a sleeve block(δl), an external bolt groove(82), and an external bolt channel(83); said square latch case(4l) having a square internal bolt bore boss(42) formed on one side surface and tap bolt holes(43) on sectional walls of opposite side surface there¬ of; said square, curved cover(46) having a square, thick, external bolt bore(47) in the center and tap bolt holes (48) at spaced locations for attaching said cover(46) to said latch case(4l) and to the circumferential surface of said sleeve(30) through said tap bolt holes(43, 48) with said washers(44) and said tap bolts(45); said elongated sliding bar(49) having a square internal bolt(50) with a U-shaped point(51 ) at one end for getting in and out of said external bolt groove(82) of said piston cylinder(δθ) , a square external bolt(54) with a U-shaped point(55) at the other end for getting in and out of said external bolt groove(82); a sliding bar block(53), a coil spring block (56), and a coil spring loading section(57) in between; said contract coil sprmg(58), with a. coil spring(73), being strong enough to yield to the highest compression force in the last stages of compression strokes and to expansion forces in the early stages of expansion strokes; said square latch case housing(31 ) comprising a sαuare, interaal bolt bore boss hole(32), an indented cover housing (33), and tap bolt holes(34) being each formed at a lower section of said sleeve(30) for keeping said external bolt (54) locked in said piston cylinder(80) longer at all possible while said piston(10) is dashing down alone to exert strong pressure;,. said internal bolt groove(19) being formed each in square shape in the lower portion of said piston(lθ) on either side for said internal .bolt(50) to lock in in suction and compression strokes and exhaust strokes; said internal bolt channel(20) with a shallow base(2l) below and a deeper base(22) above half the length of said channel (20) being formed in either side from said internal bolt groove(19) close to said pistonhead(11 ) for said internal bolt(50) to move to and to slide on said shallow base(21) by contract coil spring(58), keeping said external bolt(54) locked in said external bolt groove(82) of said piston cylinder(80) as long as possible so as to allow gas to flow through said sleeve cylinder(39) , before said internal bolt(50) slides onto said deeper base(22) to allow said external bolt(54) to get out of said external bolt groove (82), thus permitting said sleeve(30) to follow said small piston(10) to the bottom dead center smoothly; said sleeve block(81 ) being formed in a ring shape, projecting from said piston cylinder(8θ) at the top dead center for preventing said sleeve(30) from further upward movement; said external bolt groove(82) being formed in square shape in either side of said piston cylinder(80) at the top dead center so as for said external bolt(54) to lock in a little while before and in the early stage of expansion strokes; said external bolt channel(83) being formed below said external bolt groove(82) on either side and below the level of said small pιstonhead(H ) being at the bottom dead center in order not to allow gas to flow therein at the bottom dead center but to allow said external bolt(54) to pass through freely while said internal bolt(50) is sliding back from said deeper base(22), said shallow base(2l) and into said internal bolt groove(19) in exhaust strokes; said sliding bar(49) being disposed in said latch case with said internal bolt(50) projecting through said inter¬ nal bolt bore boss hole(32); said contract coil spring(58) being loaded on said loading section(57) of said external bolt(54); said cover(46) being put over said latch case (41), depressing said spnng(58) and getting said external bolt(54) in said external bolt bore(47), and joined firmly to said latch case(4l) through said tap bolt holes(<13) by said washers(44) and said tap bolts(45); said latch case (41 ) thus set up being mounted in said latch case housing (31) of said sleeve(30) with said internal bolt(50) projecting through said internal bolt bore boss hole(32) and joined to said sleeve(30) with said washers(44) and said tap bolts(45) for proper operation of said latch set (40).

Claim 6. The power output boosting engine piston of claim 4 wherein said servo cam key set(60) comprises a cam drive member of a contract coil spring-loaded pistonrod(67) being mounted in said central, upper portion of said piston(10) for causing said pistonrod(67) to reciprocate downward by gas pressure and upward by spring and a cam driven member of a tension spring loaded, close-open mouth pieces(61) being mounted in the lower portion of said piston(10) between said internal bolt groove(l9) on either side thereof for causing said mouth pieces(61 ) to be pushed open sidewise by said cam drive member(67) so as for each mouth pieee(6l) to push said internal bolt(50) out of said internal bolt groove(19) to the level of said shallow base (21) of said internal bolt channel(20) in the last stage of compression strokes and the early stage of expansion stroke for unlocking said latch set(40).

Claim 7. The power output boosting engine piston of claim 6 wherein said cam drive member comprises said pistonrod (67), a contract coil sprmg(73), a cylinder cap(74) and a cam drive member housing(l2); said pistonrod(67) having a square, V-shaped point(68) at the lower end for sliding downward between the indented, curved sidefaces(63) of said mouth pieces(6l) for perfect, easy opening of said mouth pieces(6l); a square sliding section(69); a servo piston section(70) with ring groove(7l) and πng(72); said contract coil sprmg(73), with said coil sprmg(58), being strong enough to yield only to the highest compression force in the last stage of compression strokes and in expansion strokes; said cylinder cap(74) having an externa¬ lly threaded surface for joining it firmly to said small pistonhead(11 ) and a multi-faced hole therein for allowing gas to flow through and also for use in screw driving of said cylinder cap(74); said cam drive member housing(12) having an internally threaded cylinder cap hole(17) at said pistonhead(11 ) , a servo piston cylinder(l6) being so long that said pistonhead reciprocation may open said mouth pieces(6l) to the level of said shallow base(2l), an oil passage(15) being formed each from said deeper base(22) to said servo piston cylinder(l6) , a round spring housing(14)ι and a square servo pistonrod bored3) above the central portion of said cam driven member housing(l8); said contract coil spring(73) being placed in said drive member housing(l2), said pistonrod(67) being put next therein and said cylinder cap(74) being screw driven into said cylinder cap hole(17), depressing said pistonrod(67) so as for said V-shaped point(68) to rest between said indented, curved sideface(63) of said mouth pieces(6l) in preparation for sliding down between said mouth pieces(61) to open wide in expansion strokes.

Claim 8. The power output boosting engine piston of claim 6 wherein said cam driven member comprises a pair of close-open mouth pieces(6l) and of tension springs(66), and a cam driven member housing(lδ); said mouth piece(61) having a contact sideface with angled corners(62) and an indented and curved sideface(63) in the center thereof for allowing said V-shaped point(68) of said pistonrod(67) to slide against said curved sidefaces(63) to open said mouth pieces(6l) sidewise and a tension spring housing(64) and a tension spring peg(65) being formed on either side thereof; two identical tension springs(66) being just strong enough to bring said twin mouth pieces(6l) together; said cam driven member housmg(18) being formed in square shape between said internal bolt grooves(19); said twin mouth pieces(6l) being put together, said tension spring (66) being loaded in said spring housing(64) in either side and hooked on either spring peg(65) strained; said

SUBSTITUTESHEET mouth pieces(6l) thus set up being mounted in said cam driven member housing(lδ) with said V-shaped point(68) of said pistonrod(67) resting between said indented, curved sidefaces(63) .

Claim 9. The power output boosting engine piston of claim 5 wherein, further including a plain bearing(23) being each attached to said shallow base(2l) through said deeper base(22) of said internal bolt channel(20) in either side of said piston(10) by tap bolts(24) and a roller(52) being each installed on said internal bolt points(5l) for secure, smooth slidings of said internal bolts(50).

SUBSTITUTESHEET