Title of Invention

"SPARK IGNITION FOUR -CYCLE INTERNAL COMBUSTION ENGINE WITH A SUPERCHARGING PUMP"

Abstract

To provide a spark ignition four-stroke cycle internal combustion engine with a supercharging pump having a structure in which air intake pressurized by a supercharging pump is supercharged into a combustion chamber through a supercharging valve provided separately from an air intake valve. [Means for Solving the Problem] In the spark ignition four-cycle internal combustion engine with a supercharging pump having a structure in which air supply pressurized by the supercharging pump 40 is supercharged into a combustion chamber 14 though a supercharging valve 19 provided separately from an air intake valve, the supercharging pump 40 driven by an air intake exhaust valve driving cam shaft 25 supported on the cylinder head 4is disposed on the axial line of the cam shaft 25 and connected directly to the end of the cam shaft, and the supercharging pump 40 is disposed on the opposite side end of the valve gear driving system end 33 of the air intake exhaust valve driving cam shaft 25. [Drawing Selected]

Full Text

[DETAILED DESCRIPTION OF THE INVENTION] [Technical Field of the Invention] This invention relates to a spark ignition four-cycle internal combustion engine with a supercharging pump (referred to as four-cycle internal combustion engine as so-called hereinafter) structured so that air supply pressurized by a supercharging pump is supercharged to a combustion chamber not through an intake valve but though a supercharging valve. [Prior Art] Japanese Patent Publication No. Sho_63-5562 and Japanese Kokai Publication No. Hei 7-10992J) disclose a spark ignition four-cycle internal combustion engine for supercharging pressurized air supply pressurized by a supercharging pump to a combustion chamber not though an air intake valve but though a supercharging valve. In a spark ignition four-cycle internal combustion engine disclosed in Japanese Patent Publication No. Sho 63-5562, a built-in air intake passage of a carburetor is branched to a main air intake passage and a sub air intake passage, fuel-air mixture which passes in the main air intake passage is supplied to a combustion chamber of an internal combustion engine though a reed valve and main intake valve, on the other hand, fuel-air mixture which passes the sub air intake passage is pressurized by supercharging pump and supplied to the combustion chamber through a sub air intake valve.In a spark ignition four-cycle internal combustion engine disclosed in Japanese Patent Kokai Publication No. Hei 7-109929, each upstream of a main air intake passage and sub air intake passage which are formed in parallel is connected to an air cleaner respectively, and each downstream end of the main air intake passage and the sub air intake passage is connected respectively to the combustion chamber of an internal combustion engine through an intake valve, the main air intake passage is provided with a carburetor and the sub air intake passage is provided with a reciprocating type supercharging pump. [Problem to be Solved by the Invention] In the spark ignition four-cycle internal combustion engine disclosed in Japanese Patent Publication No. Sho 63-5562, because an supercharging pump is provided on a cylinder head where an intake valve is provided, and connected to a cam shaft with interposition of a transmission member, a passage volume through which the pressurized fuel-air mixture passes is not so much increased, and the response speed is high, however, the required transmission system results in a complex structure and a large-sized internal combustion engine as a whole. In the spark ignition four-cycle internal combustion engine disclosed in Japanese Patent Kokai Publication No. Hei-7-109929, because air intake is supercharged by reciprocal motion of a piston connected to a crank shaft of an internal combustion engine, the air intake passage volume of the space from a supercharging pump to the intake valve is large, and the response speed and efficiency are poor, and a large-sized supercharging pump is required to secure a certain quantity of supercharging supply because the reciprocating type supercharging pump is a single acting type pump. [Means for Solving the Problem and Effects] The present invention relates to modification of a spark ignition four-cycle internal combustion engine with a supercharging pump form which the above-mentioned problems are solved, the invention described in claim 1 provides a spark ignition four-cycle internal combustion engine with a supercharging pump having a structure in which air supply pressurized by a supercharging pump is supercharged to a combustion chamber not through an intake valve but through a supercharging valve, wherein the spark ignition four-cycle internal combustion engine with a supercharging pump has a supercharging pump driven by a intake and exhaust valve driving cam shaft supported on a cylinder head located on the axis line of the cam shaft. Because the spark ignition four-cycle internal combustion engine with a supercharging pump described in claim 1 is structured as described in claim 1, the air intake passage from the supercharging pump to the air intake valve is short, the reduced passage volume results in improved response speed and efficiency. By structuring the spark ignition four-cycle internal combustion engine with a supercharging pump of the present invention as described in claim 2, the power transmission system between the cam shaft and supercharging pump is eliminated, the elimination leads to a simplified and compact structure, and leads to a reduced cost. Further, by structuring the spark ignition four-cycle internal combustion engine with a supercharging pump of the present invention as described in claim 3, the supercharging pump can be provided near the intake and exhaust valve without interference with a valve gear driving system of an intake valve driving cam shaft, the cylinder head of an internal combustion engine is structured compact, and thus an internal combustion engine can be further made small sized. Yet further, by structuring the spark ignition four-cycle internal combustion engine with a supercharging pump of the present invention as described in claim 4, a supercharging pump can be further made small sized. By structuring the spark ignition four-cycle internal combustion engine with a supercharging pump of the present invention as described in claim 5, fuel in fuel-air mixture is dispersed homogeneously in the supercharging pump. By structuring the spark ignition four-cycle internal combustion engine with a supercharging pump of the present invention as described in claim 6, the intake period of a normal intake without supercharging is extended, and spitting due to pressurized supercharging air supply is prevented, thus trapping efficiency is greatly improved. Accordingly, the present invention relates to a spark ignition four-cycle internal combustion engine with a supercharging pump having a structure in which air supply pressurized by a supercharging pump is supercharged to a combustion chamber not through an intake valve but through a supercharging valve, said spark ignition four-cycle internal combustion engine with a supercharging pump having a supercharging pump driven by an intake and exhaust valve driving cam shaft supported on a cylinder head located on the axis line of said cam shaft [BRIEF DESCRIPTION OF THE/DRAWINGS] FIG. 1 is a longitudinal sectional view of an embodiment of an air-cooled overhead valve type internal combustion engine in accordance with the present invention. FIG. 2 is a horizontal sectional view along the line II -II in FIG. 1. FIG. 3 is a plan view of a supercharging pump shown in FIG. 1. FIG. 4 is a view in the direction of the arrow IV in FIG. 3. FIG. 5 is a longitudinal sectional view along the line V-V in FIG. 3 . FIG. 6 is a longitudinal sectional view along the line VI-VI in FIG. 5. FIG. 7 is a longitudinal sectional view along the line VH-VII in FIG. 6. FIG. 8 is a view from the direction of the arrow VIII-VIII in FIG. 5. FIG. 9 is a view from the direction of the arrow IX-IX in FIG. 6. FIG. 10 is a set of exploded component views of an intake exhaust lead valve of a supercharging pump. FIG. 11 is a characteristic chart for describing the open-close timing of a supercharging valve, an air intake valve, and an exhaust valve in the embodiment shown in FIG. 1. FIG. 12 is a longitudinal sectional view of another embodiment of the present invention. [Preferred Embodiments] An embodiment of the present invention will be described in detail hereinafter with reference to FIG. 1 to FIG. 10. An air-cooled overhead valve spark ignition single cylinder four-cycle internal combustion engine 1 is mounted on a motorcycle not shown in the drawings so that a crank shaft is directed in the width direction of the motorcycle, a cylinder block 3, a cylinder head 4, and a cylinder head cover 5 are placed one on another on a crank case 2 , and the crank case 2, the cylinder block 3, the cylinder head 4, and the cylinder head cover 5 are combined each other with a through bolt 6. As shown in FIG. 2, the crank shaft 7 is supported on the crank case 2 rotatably, a piston 9 is inserted to a cylinder hole 8 of a cylinder block 3 slidably toward up and down, the both ends of the connecting rod 12 is fixed rotatably to the piston pin 10 of the piston 9 and to the crank pin 11 of the crank shaft 7, in the combustion chamber 14 which is defined by the approximately hemispherical concave surface 13 of the central under surface of the cylinder head 4, the side wall of the cylinder hole 8 of the cylinder block 3, and the top surface of the piston 9, the piston 9 is pressed downward by combustion gas ignited intermittently with a spark plug 15 at the timing near the top dead center of the cylinder hole 8, and thus the crank shaft 7 is driven for rotation by the pressure force. Further as shown in FIG. 1, the spark plug 15 and a supercharging port 16 are provided through the cylinder head 4 along the plane passing through respectively the center line of the crank shaft 7 and the cylinder hole 8, and as shown in FIG. 2, an air intake port 17 and an exhaust port 18 are provided along a plane perpendicular to the above-mentioned plane which passes through the center line of the cylinder hole 8, the supercharging port 16, air intake port 17, and exhaust port 18 are provided respectively with a supercharging valve 19, an air intake valve 20, and an exhaust valve 21 which are open-and-close operated. Further, as shown in FIG. 1, a cam shaft 25 is fixed rotatably to the combustion chamber 4 with interposition of an angular ball bearing 26 and a ball bearing 27 with offset of the cam shaft 25 from an air intake valve 20 having a large diameter side to an exhaust valve 21 side with respect to the center line of the cylinder hole 8. As shown in FIG. 2, rocker-arm shafts 28 and 29 are supported through the cylinder head 4 in parallel to the cam shaft 25 at the position symmetrical and distant equally to the cam shaft 25, the rocker-arm shafts are provided respectively with rocker-arms 30 and 31 supported swingably thereon, the crank shaft 7 is provided with a drive sprocket 32 fixed solidly thereto, a driven sprocket 33 with the number of teeth double that of the drive sprocket 32 is fixed solidly to the cam shaft 2 with a bolt 34, an endless chain 35 is hung between the drive sprocket 32 and driven sprocket 33, and the supercharging valve 19, air intake valve 20, and exhaust valve 21 are open-and-close operated at the timing as shown in FIG. 11 once every two clock-wise revolution in FIG. 2 of the crank shaft 7. Two shims 36 are fit on the outer periphery of the cam shaft 25 at the position outside the angular ball bearing 26, and outside the shims, a supercharging cam 37 is fixed to the cam shaft 25 with a key so as not to be rotated relatively in the circumferential direction, a bolt 38 is screwed in a center tapped hole (anti-clockwise screw) of the cam shaft 25 at the position further outside the supercharging cam 37, and when a force which prevents the cam shaft 25 from rotating in the clockwise direction in FIG. 2 is applied to the bolt 38, the bolt 38 is tightened into the center tapped hole and the supercharging cam 37 is strongly tightened against the angular ball bearing 26 with interposition of the shim 36. A cam shaft fixing bolt 78 is screwed fixedly to the head cover which covers the left side of the cylinder head 4 in FIG. 1, the end (right end) of the cam shaft fixing bolt 78 is in contact with the end of the cam shaft 25 with interposition of a ball 79, and by screwing in the cam shaft fixing bolt 78 and fixing the cam shaft fixing bolt 78 with a lock nut 80, the cam shaft 25 is fixed so as not to move in the axial direction with the angular ball bearing 26 and the cam shaft fixing bolt 78. As shown in FIG. 1 and FIG. 3, a cylinder case 41 of the supercharging pump 40 is fixed solidly with a bolt 43 with interposition of a pump fixing block 39 on the right of the cylinder head 4, and as shown in FIG. 5 and FIG. 6 in detail, a piston 44 is inserted slidably in the cylinder hole 42 of the cylinder case 41, a crank shaft 45 is supported rotatably on the cylinder case 41 with interposition of a seal bearing 46, the end of the crank shaft 45 is spline-inserted in a head center hole 38a of a bolt 38 screw-fixed to the cam shaft 25, both ends of the connecting rod are inserted rotatably to a piston pin 47 inserted in the piston 44 and to a crank pin 48 inserted in the crank shaft 45 with interposition of ball bearings 50 and 51 respectively, and when the crank shaft 45 combined solidly with the cam shaft 24 is rotated, the piston 44 is reciprocated. The cylinder case 41 and piston 44 of the supercharging pump 40 are divided into two parts with respect to the center of the axial length, the divided cylinder case 41 is combined solidly each other with the pump fixing block 39 and the bolt 43, and as shown in FIG. 6, the divided piston 44 is combined solidly each other with a bolt 52, but partitioned into two cylinder chambers 53 by the piston 44. i On both ends of the cylinder case 40, an intake valve junk ring 54, an intake reed valve 55, a reed valve base 56, a discharge reed valve 57, and a cap 58 are placed one upon another as shown in FIG. 8 to FIG. 10, a knock pin 60 extending though the intake valve junk ring 54 and the intake reed valve 55 is inserted into a blind hole of the reed valve base 56, the knock pin 61 extending through the discharge reed valve 57 is inserted into a blind hole of the reed valve base 56 and the cap 58, the intake valve junk ring 54, the intake reed valve 55, the reed valve base 56, and discharge reed valve 57 are fixed to the cylinder case 40 and the cap 58 so as not to be rotated round the center of the axial line of the cylinder case 40, and these intake valve junk ring 54, the intake reed valve 55, the reed valve base 56, the discharge reed valve 57, and the cap 58 is fixed solidly to the cylinder case 40 with a bolt 59 (refer to FIG. 7) which is screw-fixed to the cap 58 located at the under position extending through the cap 58 and the cylinder case 40 located at the upper position. As shown in FIG. 10, the intake lead valve 55 is provided with four leads 55a extending from the periphery to the center of the intake reed valve 55, the free end of a reed 55a is structured so as to close an intake hole 56a of the reed valve base 56. Further, the discharge reed valve 57 is provided with semi-circular slits 57a, and the central reed 57b closes discharge holes 56b of the reed valve base 56. The intake reed valve 55 is provided with slotted holes 55b to communicate to the discharge holes 56b of the reed valve base 56. As shown in FIG. 5 and FIG. 6, at the intermediate between the reed valve base 56 and the cap 58, an intake chamber 62 is formed, a discharge chamber 63 (refer to FIG. 6) is formed between the periphery of the lead valve base 56 and the cap 58, and communication blocks 64 are fixed solidly to one side of the top and bottom caps 58 with a bolt 65, the top and bottom ends of the intake communication block 64 and discharge communication pipe 67 are fixed to the top and bottom communication blocks 64, the one intake chamber 62 is communicated to the other intake chamber 62 through an intake communication passage 68 and an intake communication pipe 66 formed on the cap 58 and the communication block 64 respectively, and the one discharge chamber 63 is communicated to the other discharge chamber 63 through a discharge passage 69 and the discharge communication pipe 67 formed on the cap 58 and the communication block 64 respectively. An intake passage (not shown in the drawing) is formed in the front-rear and horizontal direction from the intake communication passage 68 located at the bottom communication block 64, the intake passage is connected to the carburetor 11 (not shown in the drawing) through a communication pipe not shown in the drawing, a discharge passage 71 is formed along the right-left horizontal direction directing from the discharge communication passage 69 located on the bottom communication block 64 to the cylinder head 4 , and as shown in FIG. 1, FIG. 3, and FIG. 4, the discharge passage 71 is connected to the supercharging port 16 through a pipe joint bolt 72 and communication pipe 73, air-fuel mixture mixed with fuel in the carburetor is charged into the top and bottom cylinder chambers 53 through the intake passage, the intake communication passage 68, intake communication pipe 66, the intake chamber 62, the intake reed valve 55, and the intake hole 56a of the reed valve base 56, and the air-fuel mixture is pressurized by vertical motion of the piston 44, and is charged into the supercharging port 16 through the discharge hole 56b of the reed valve base 56 , the discharge reed valve 57, the discharge chamber 63, the discharge communication pipe 67, discharge communication passage 69, the discharge passage 71, the communication passage 73, and the pipe joint bolt 72, and when the supercharging valve 19 is operated to open, fuel-air mixture is supplied into the combustion chamber 14 in an amount 150 % stroke volume (150 % is an example, the percentage may be larger or smaller) of the air-cooled overhead valve spark ignition single cylinder four-cycle internal combustion engine 1. As shown in FIG. 6, a shallow concave 42a is formed on the wall of the cylinder hole 42 near the seam of the cylinder case 41 which is divided into the top and bottom two portions, the intake communication pipe 66 is fitted to a relief block 74 so as to cover the hole 66a formed at the middle in the longitudinal direction of the intake communication pipe 66, the commutation hole 41a which communicates between a space 74a of the relief block 74 and the concave 42a of the cylinder hole 42 is formed on the cylinder case 41, a relief valve 75 which is possible to be in contact with the opening of the communication hole 41a is provided in the space 74a of the relief block 74, the relief valve 75 is pressed onto the opening of the communication hole 41a by the spring force of a compression coil spring 76, air-fuel mixture is pressurized by reciprocation motion of the piston 44 to be charged in the space 44a in the piston 44, and the pressurized air-fuel mixture passes from a side opening 44b of the piston 44 to the concave 42a of the cylinder hole 42 and a communication hole 41a of the cylinder case 40, and discharged into the intake communication pipe 66 though the space of the relief block 74 and a hole 66a of the intake communication pipe 66. As shown in FIG. 1, a soft seal member 77 made of rubber or synthetic plastics is fitted on the surface of the valve guide 22 which is exposed in the supercharging port 16 and on a stem member 19a of the supercharging valve 19 which projects from the valve guide 22, a band 77a is fitted on the peripheral surface of the soft seal member 77 to prevent the soft seal member 77 from falling. The embodiment shown in FIG. 1 to FIG. 10 is structured as described herein above, in the operation of the air-cooled overhead valve spark ignition single cylinder four-cycle internal combustion engine 1, the air intake valve 20 and the exhaust valve 21 are operated to open and close at the timing as shown in FIG. 11 during two revolution of the crank shaft 7, and also the supercharging valve 19 is driven to open and close, fuel-air mixture charged into the combustion chamber 14 by operating the air intake valve 20 to open and pressurized fuel-air mixture supercharged into the combustion chamber 14 by operating the supercharging valve 19 to open are ignited with a spark of the spark plug 15 at the timing near the top dead center, expansion of the combustion gas lowers the piston 9 to rotating-drive the crank shaft 7 with interposition of the connecting rod 12 . Because the supercharging pump 40 is directly connected to the cam shaft 25, the driving system of the supercharging pump 40 has a very simple structure. Further, because the supercharging pump 40 is located on the end of the cam shaft 25 located opposite side to the driven sprocket 33 of the valve gear system, the structure near the cam shaft 25 is simplified. Because the supercharging pump 40 is located near the combustion chamber 14 of the air-cooled overhead valve spark ignition single cylinder four-cycle internal combustion engine 1, the supercharging passage from the supercharging pump 40 to the combustion chamber 14 is greatly shortened, and the supercharging efficiency and response speed is maintained at a high level. Further as shown in FIG. 9, pressurized fuel-air mixture pressurized by the supercharging pump 40 is supplied into the combustion chamber 14 with opening of the supercharging valve 19 at the timing near the bottom dead center when an intake stroke of fuel-air mixture with opening of the air intake valve 20 is almost completed, the pressurized fuel-air mixture will not be spat from the air intake valve 20 to the upstream air intake passage, fuel-air mixture is supercharged smoothly to the air-cooled overhead valve spark ignition single cylinder four-cycle internal combustion engine 1 without increased cubic capacity, and the output can be very high. Because the supercharging pump 40 is double acting type, even if the cam shaft 25 and crank shaft 45 of the supercharging pump 40 are rotated at a rotation speed half that of the crank shaft 7 of the air-cooled overhead valve spark ignition single cylinder four-cycle internal combustion engine 1, pressurized fuel-air mixture is supercharged sufficiently into the combustion chamber 14 due to high supercharging capacity in comparison with the whole size of the supercharging pump 40. Because the supercharging pump 40 is provided with the intake lead valve 55 and the discharge lead valve 57 which are operated automatically to open and close correspondingly to the pressure difference, the structure can be simplified and made compact, and leads to a reduced cost. A tappet clearance between the supercharging valve 19 and the supercharging cam 37 is adjustable very simply and properly by moving the supercharging cam 37 in the axial direction with respect to the cam shaft 25 with replacing the shim 36 having different thickness. Further, because the seal member 77 is provided on the stem member 19a of the supercharging valve 19 and on the surface 16a of the supercharge port 16 side of the valve guide 22, pressurized fuel-air mixture in the supercharge port 16 presses the seal member 77 onto the supercharge port 16 side surface of the valve guide 22, the clearance between the stem member 19a of the supercharging valve 19 and the valve guide 22 is sealed, and leakage of fuel-air mixture is prevented. When the supercharging valve 19 is opened, the exhaust valve 21 is closed, and pressurized fuel-air mixture having a pressure higher than exhaust gas in the combustion chamber 14 is charged into the supercharge port 16, such condition prevents exhaust gas in the combustion chamber 14 from leaking into the supercharge port 16, and the seal member 77 will not be damaged due to high temperature exhaust gas.Because the supercharge port 16 and the air intake port 17 are located so that the extension line of the supercharge port and the extension line of the air intake port 17 are orthogonal in the top view and the extension lines intersect each other, fuel-air mixture is mixed homogeneously and a spark goes from the spark plug toward the intersection, such condition facilitates smooth ignition. In the embodiment shown in FIG. 1 to FIG. 10, the crank shaft 45 of the supercharging pump 40 connected directly to the cam shaft 25 is connected to the piston with interposition of the connecting rod 49, however, as shown in FIG. 12 a structure in which a small diameter member 45a of the crank shaft 45 of the supercharging pump connected directly to the cam shaft 25 is fixed in a longitudinal groove (in the direction perpendicular to the paper plane) of the piston 44 as shown in FIG. 12 may be used. Also such structure may be used for reciprocating motion of the piston to rotate the crank shaft 45. In the air-cooled overhead valve spark ignition single cylinder four-cycle internal combustion engine 1 shown in FIG. 11, the top end of the stems 20a and 21a of the air intake valve 20 and the exhaust valve 21 located on the right and left corresponds respectively to the cam tops 25a and 25b of the reference conical surface, the top end of the stem 19a of the supercharging valve 19 is brought into contact with the cam top 25c of the reference cylindrical surface, and only the cam top 25 b is adjustable in the axial direction with respect to the cam shaft 25, however, if the cam top 25a is structured so as to be adjustable in the axial direction, then the tappet clearance of the air intake valve 20 and the exhaust valve 21 becomes easily adjustable. In the air-cooled overhead valve spark ignition single cylinder four-cycle internal combustion engine 1 shown in the drawings, fuel-air mixture which is formed by mixing previously air and fuel in the carburetor is supplied to the combustion chamber 14, this invention may be applied to an internal combustion engine having a structure in which only air is supplied instead of fuel-air mixture and fuel is injected directly into the combustion chamber 14. [DESCRIPTION OF REFERENCE CHARACTERS] 1 ... AIR-COOLED OVERHEAD SPARK IGNITION SINGLE CYLINDER FOUR-CYCLE INTERNAL COMBUSTION ENGINE 2 ... CRANK CASE 3 ... CYLINDER BLOCK 4 ... CYLINDER HEAD 5 ... CYLINDER HEAD COVER 6 ... BOLT 7 ... CRANK SHAFT 8 ... CYLINDER HOLE 9 ... PISTON 10 ... PISTON PIN 11 ... CRANK PIN 12 ... CONNECTING ROD 13 ... SEMICIRCULAR CONCAVE 14 ... COMBUSTION CHAMBER 15 ... SPARK PLUG 16 ... SUPERCHARGE PORT 17 ... AIR INTAKE PORT 18 ... EXHAUST PORT 19 ... SUPERCHARGING VALVE 20 ... AIR INTAKE VALVE 21 ... EXHAUST VALVE 22, 23, AND 24 ... VALVE GUIDE 25 ... CAM SHAFT 26 ... ANGULAR BALL BEARING 27 ... BALL BEARING 28 AND 29 ... ROCKER ARM SHAFT 30 AND 31 ... ROCKER ARM 32 ... DRIVE SPROCKET 33 ... DRIVEN SPROCKET 34 ... BOLT 35 ... ENDLESS CAM CHAIN 36 ... SHIM 37 ... SUPERCHARGE CAM 38 ... BOLT 39 ... PUMP FIXING BLOCK 40 ... SUPERCHARGING PUMP 41 ... CYLINDER CASE 42 ... CYLINDER HOLE 43 ... BOLT 44 ... PISTON 45 ... CRANK SHAFT 46 ... SEAL BEARING 47 ... PISTON PIN 48 ... CRANK PIN 49 ... CONNECTING ROD 50 AND 51 ... BALL BEARING 52 ... BOLT 53 ... CYLINDER CHAMBER 54 ... INTAKE VALVE JUNK RING 55 ... INTAKE REED VALVE 56 ... REED VALVE BASE 57 ... DISCHARGE REED VALVE 58 ... CAP 59 ... BOLT 60 AND 61 ... KNOCK PIN 62 ... INTAKE CHAMBER 63 ... DISCHARGE CHAMBER 64 ... COMMUNICATION BLOCK 65 ... BOLT 66 ... INTAKE COMMUNICATION PIPE 67 ... DISCHARGE COMMUNICATION PIPE 68 ... INTAKE COMMUNICATION PASSAGE 69 ... DISCHARGE COMMUNICATION PASSAGE 71 ... DISCHARGE PASSAGE 72 ... PIPE JOINT BOLT 73 ... COMMUNICATION PIPE 74 ... RELIEF BLOCK 75 ... RELIEF VALVE 76 ... COMPRESSION COIL SPRING 77 ... SEAL MEMBER 78 ... CAM SHAFT FIXING BOLT 79 ... BALL 80 ... LOCK NUT We Claim: 1. A spark ignition four-cycle internal combustion engine (1) with a supercharging pump (40) having a structure in which air supply pressurized by a supercharging pump (40) is supercharged to a combustion chamber (4) not through an intake valve (20) but through a supercharging valve (19), said spark ignition four-cycle internal combustion engine (1) with a supercharging pump (40) having a supercharging pump (40) driven by an intake (20) and exhaust (21) valve driving cam shaft (25) supported on a cylinder head (4) located on the axis line of said cam shaft (25). 2. A spark ignition four-cycle internal combustion engine with a supercharging pump (40) as claimed in claim 1, wherein said supercharging pump (40) is directly connected to the end of said cam shaft (25). 3. A spark ignition four-cycle internal combustion engine with a supercharging pump (40) as claimed in claim 1 or claim 2, wherein said supercharging pump (40) is located on the opposite end of the valve gear driving system of said intake (20) and exhaust (21) valve driving cam shaft (25). 4. A spark ignition four-cycle internal combustion engine with a supercharging pump (40) as claimed in any one of claims 1 to 3, wherein said supercharging pump is a reciprocating double-acting pump, and directly connected to said intake (20) and exhaust (21) valve driving cam shaft (25) with interposition of a crank mechanism. 5. A spark ignition four-cycle internal combustion engine substantially as hereinbefore described with reference to the accompanying drawings. 2.

Documents:

1796-del-1998-abstract.pdf

1796-del-1998-claims.pdf

1796-del-1998-correspondence-others.pdf

1796-del-1998-correspondence-po.pdf

1796-del-1998-description (complete).pdf

1796-del-1998-drawings.pdf

1796-del-1998-form-1.pdf

1796-del-1998-form-13.pdf

1796-del-1998-form-19.pdf

1796-del-1998-form-2.pdf

1796-del-1998-form-3.pdf

1796-del-1998-form-4.pdf

1796-del-1998-form-6.pdf

1796-del-1998-gpa.pdf

1796-del-1998-petition-137.pdf

1796-del-1998-petition-138.pdf

abstract.jpg