WO1983000722A1 - Soupape rotative de moteur avec systeme de lubrification et joints ameliores - Google Patents

Soupape rotative de moteur avec systeme de lubrification et joints ameliores Download PDF

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Publication number
WO1983000722A1
WO1983000722A1 PCT/US1981/001099 US8101099W WO8300722A1 WO 1983000722 A1 WO1983000722 A1 WO 1983000722A1 US 8101099 W US8101099 W US 8101099W WO 8300722 A1 WO8300722 A1 WO 8300722A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
cylinder
head
piston
circumferentially
Prior art date
Application number
PCT/US1981/001099
Other languages
English (en)
Inventor
Phillip Rodney Hopkins
Original Assignee
Phillip Rodney Hopkins
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Phillip Rodney Hopkins filed Critical Phillip Rodney Hopkins
Priority to EP19810902358 priority Critical patent/EP0086190A1/fr
Priority to PCT/US1981/001099 priority patent/WO1983000722A1/fr
Publication of WO1983000722A1 publication Critical patent/WO1983000722A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L7/00—Rotary or oscillatory slide valve-gear or valve arrangements
    • F01L7/02—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves
    • F01L7/026—Rotary or oscillatory slide valve-gear or valve arrangements with cylindrical, sleeve, or part-annularly shaped valves with two or more rotary valves, their rotational axes being parallel, e.g. 4-stroke

Definitions

  • This invention relates to an improved valve mean for an internal combustion engine.
  • This invention is of a shaft-type valve wherein there are diametrical passageways arranged in the shaft which spans the cylinder and through which intake and exhaust takes place and wherein the openings or holes in the shaft are of predetermined size and this size in the circumferential distance is substantially equal to 1/16 of the circumference of the shaft, as is set forth more fully hereinafter.
  • the rotary valve is different from prior art valves in that a direct travel of intake and exhaust is through the shaft which allows a continuous rotary motion of the shaft with correct timing for a four cycle piston engine.
  • the timing is possible because the width circumferentially of the opening is substan ⁇ tially 1/16 of the circumference of the shaft.
  • the problems of prior art rotary valves are primarily that they do not seal an explosive mixture and allow gas to escape.
  • the shaft of the instant invention has both longitudinal and circular seals to prevent gas from escaping-
  • the advantages of the instant invention are the - elimination of valve springs and popet type valves that currently require in the order of about 10% or more of the delivered qr produced horse power of the engine. There is a direct and unobstructed intake and exhaust flow and no valve face in the path of the
  • OMPI /,, V/IPO mixture as in current engines.
  • the components are of a structure which permits them to be very strong and there is a reduction in the number of working parts by reason of the utilization of the instant invention.
  • the system is adaptable for virtually all four cycles piston engines and is adapted to work well with fuel injection and stratified charge heads. It is also useful for diesel fuel where very high compression ratios are required.
  • the shafts and seal of the instant invention replace a large number of parts, estimated to be in the range of about 80, which are normally utilized to accomplish the same effect in a normal V8 engine reducing the expense of such engines.
  • the engine is capable of turning at increased rpm's with a resultant higher horse power from the same displacement- Also, when used with the stratified charge type engine, the rich charge chamber can be shaped more efficiently than with normal engines which yields a greater degree of horse power for less polluting gases since the same are combusted more thoroughly.
  • This invention provides for a shaft having improved seals and improved lubrication system for the shaft which serves as a rotary valve, and a wiper-type acting bar-type seals urged into engage ⁇ ment with the interior of the head but carried by the rotating shaft to provide for a smooth distribution of oil and sealing of the shaft valve as is set forth more fully hereinafter.
  • Figure 1 is a side elevation view in cross section of an internal combustion engine of the four cycle type
  • Figure 2 is a partial view taken on the plane indicated by the line 2-2 of Figure 1 and looking in the direction of the arrows;
  • Figure 3 is a plan view in cross section of the upper zone of Figure 1;
  • Figure 4 is a shaft as described hereinafter for use in a one cylinder engine
  • Figure 5 is a view in cross section of the shaft taken on the plane indicated by the line 5-5 of Figure 4;
  • Figure 6 is an elevation view of the bar seal 501 seen in the embodiment of Figure 2;
  • Figure 7 is an end view of the bar seal of Figure 6;
  • Figure 8 is an elevation view of the leaf spring utilized to urge the bar seal outwardly.
  • Figure 9 is an end view of the spring shown in Figure 8.
  • an in- ternal combustion engine generally designated by the numeral 12. It is composed of a block 14 having a lower end spanned by an oil pan 16 in open communi ⁇ cation with the lower end of cylinders, such as that designated by the numeral 20 with the oil pan being secured to the block by suitable means, such as the bolt 21.
  • the upper end of the block is provided with a head 18.
  • pistons 22 are recip ⁇ rocal in the cylinder 20, for example, being connect ⁇ ed by a rod, such as that designated by the numeral 24 to a crank shaft 28 as at 26, and, specifically to an eccentric portion thereof.
  • the end 30 of the crank shaft is connected by a suitable means to a power takeoff and, at the other end, 32, a gear or other drive means is provided -for engaging a belt, chain, or other type of force transmission means to
  • the shaft 36 is rotatable within a tunnel through the head, generally designated by the numeral 41 and wherein there is an opening on the opposite sides in diametrical relation as at 43 and 53.
  • the head is provided with a pair of coplanar surfaces 70 and 71 which abut the upper surface 73 of the block and are suitably secured thereto as by the bolts 75 and 77.
  • the upper portion 40 of the head which spans the piston cylinders is 0 elevated, as at 46 in the central longitudinally extending zone and curves downwardly and outwardly to the portions 70 and 71 on the block 73 as designated by the numerals 45 and 45' and through which the opening 43 is located in the case of the shaft 36.
  • each of the shafts 0 has a through bore as at 90 and 92 which is diametri ⁇ cal and extends completely across it and is of a diameter which is substantially one-sixteenth of the circumference of the shaft, one of which will be referred to as the intake shaft and one of which will 5 be referred to as the output shaft.
  • a bore 101 is provided for a spark plug 50 which will be utilized to ignite a fuel mixture which will be introduced and exhausted
  • the intake shaft the one on the right in Figure 2, this will be referred to as the intake shaft and it serves as an intake valve.
  • a fuel and air mixture is introduced into the hood 201 having the opening 203 leading into the tunnel so that when fuel and " air are introduced through the opening 205, and the shaft is lined up with the opening 53, fuel will pass through and out the opening 43 and into the chamber 103.
  • this opening in the shaft is one-sixteenth of the circumference of the shafts 36 and 37, which are equal in the preferred embodiment, i.e., the distance between the relatively long sides 403 and 405, and these are sized to cover approximately 80% of the diameter of the cylinder and piston and preferably at least as great as the radius of the cylinder.
  • Seal means are pro ⁇ vided on each of the shafts. These seal means are of two types: As shown in Figure 2, circumferential
  • seal member 501 comprising a bar having an outer surface 503 in engagement with the inner surface of the head at all times in rotation and this provides a sweeping action against the inner surface of the head providing seal means to prevent blow by.
  • Additional seal means are provided between each of the cylinders and between the bearings, as shown in Figure 1, 42 and the en ⁇ larged portion of the shaft 36, this seal means being Q designated by the numeral 601 and resisting any type of blow by axially.
  • These seal means may resemble conventional piston rings and are seated in grooves located appropriately in the shafts.
  • the embodiment of Figures 4 and 5 is of a device 5 according to the above description and utilized in a one.cylinder engine. New numbers will be assigned to follow the description of Figures 4 through 9.
  • the shaft 702 has a diametrical through bore 704 and the peripherally spaced circumferential slots 706, 708, 0 7 0 and 712 which are arranged with respect to the radius at the angle shown in the drawings and which generally traces a depthwise chord as opposed to a radial line.
  • a bar seal 714, shown in Figures 6 and 7, is sized to snugly seat in each of these recesses and is adapted to be urged outwardly by the spring shown in Figures 8 and 9.
  • the bar seal has a beveled or wiper surface 716 adapted for windshield wiper engagement with the interior of the bore within which the shaft rotates.
  • the bar is urged outwardly by a g spring 718 which is in each of the recesses and urges the bar seated in it into sweeping engagement with the wall of the engine as it rotates and the seal is carried by the shaft.
  • the oil distribution means 902 shown in Figure 2 is utilized 5 to distribute oil along the length of the shaft.
  • longitudinally extending passageways are provided in the groove for lubrication between the exterior surface of the shaft
  • This invention finds use in four cycle (Otto cycle) internal combustion engines. Suitable openings, shown through the shafts, and in the engine block are provided for water cooling of the same.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Abstract

Soupape du type à tige (36) pour un moteur à combustion interne du type ayant un bloc (14) dans lequel est aménagé un cylindre et un piston (22) en mouvement alternatif dans le cylindre, où la chambre est recouverte par une culasse (18), et une soupape améliorée ayant la forme d'une tige (36) tourillonnée dans la culasse, une partie de la tige enjambant une partie du cylindre au-dessus du piston, et la tige possède un passage diamétral (90, 92) ayant une section qui, dans la direction de la ligne médiane de la tige, est au moins aussi grande que le rayon du cylindre et dont la circonférence est une distance sensiblement égale à 1/16 de la circonférence de la tige, et où des moyens de joints (501) sont prévus entre la tige et le moteur, et un vilebrequin (30) relié au piston est relié à la tige (36) pour la faire tourner simultanément avec le vilebrequin par un moyen de transmission de force (38) tel qu'une courroie ou autre.
PCT/US1981/001099 1981-08-17 1981-08-17 Soupape rotative de moteur avec systeme de lubrification et joints ameliores WO1983000722A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP19810902358 EP0086190A1 (fr) 1981-08-17 1981-08-17 Soupape rotative de moteur avec systeme de lubrification et joints ameliores
PCT/US1981/001099 WO1983000722A1 (fr) 1981-08-17 1981-08-17 Soupape rotative de moteur avec systeme de lubrification et joints ameliores

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/US1981/001099 WO1983000722A1 (fr) 1981-08-17 1981-08-17 Soupape rotative de moteur avec systeme de lubrification et joints ameliores

Publications (1)

Publication Number Publication Date
WO1983000722A1 true WO1983000722A1 (fr) 1983-03-03

Family

ID=22161371

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/US1981/001099 WO1983000722A1 (fr) 1981-08-17 1981-08-17 Soupape rotative de moteur avec systeme de lubrification et joints ameliores

Country Status (2)

Country Link
EP (1) EP0086190A1 (fr)
WO (1) WO1983000722A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2076063A2 (es) * 1992-04-24 1995-10-16 Santiago Antonio Serralvo Perfeccionamientos introducidos en motores de explosion.
US5579730A (en) * 1996-02-09 1996-12-03 Trotter; Richard C. Rotary valve head assembly and related drive system for internal combustion engines
US6443116B1 (en) 1998-08-13 2002-09-03 Ab Dafab Valve device for an internal combustion engine
ES2242549A1 (es) * 2005-04-14 2005-11-01 Antonio Ferreres Lopez Valvula de distribucion rotativa para motores termicos cuatro tiempos a propulsion de hidrogeno.
ITPA20100018A1 (it) * 2010-04-20 2011-10-21 Vincenzo Adamo Sistema di distribuzione a flauti.

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1286967A (en) * 1917-09-22 1918-12-10 Henry Eschwei Valve mechanism for engines.
US1513911A (en) * 1922-01-28 1924-11-04 Clyde W Keller Internal-combustion engine
FR634572A (fr) * 1926-09-22 1928-02-20 Moteur sans soupapes à quatre temps à distributeur rotatif
US1971060A (en) * 1932-04-22 1934-08-21 Mary C Wills Rotary valve
US2183024A (en) * 1938-03-30 1939-12-12 William W Large Rotary valve for engines
FR1037297A (fr) * 1951-05-19 1953-09-15 Distribution rotative pour moteur à explosion à quatre temps
CH354622A (fr) * 1957-11-22 1961-05-31 Mottet Armand Moteur à combustion interne à piston

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1286967A (en) * 1917-09-22 1918-12-10 Henry Eschwei Valve mechanism for engines.
US1513911A (en) * 1922-01-28 1924-11-04 Clyde W Keller Internal-combustion engine
FR634572A (fr) * 1926-09-22 1928-02-20 Moteur sans soupapes à quatre temps à distributeur rotatif
US1971060A (en) * 1932-04-22 1934-08-21 Mary C Wills Rotary valve
US2183024A (en) * 1938-03-30 1939-12-12 William W Large Rotary valve for engines
FR1037297A (fr) * 1951-05-19 1953-09-15 Distribution rotative pour moteur à explosion à quatre temps
CH354622A (fr) * 1957-11-22 1961-05-31 Mottet Armand Moteur à combustion interne à piston

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2076063A2 (es) * 1992-04-24 1995-10-16 Santiago Antonio Serralvo Perfeccionamientos introducidos en motores de explosion.
US5579730A (en) * 1996-02-09 1996-12-03 Trotter; Richard C. Rotary valve head assembly and related drive system for internal combustion engines
US6443116B1 (en) 1998-08-13 2002-09-03 Ab Dafab Valve device for an internal combustion engine
ES2242549A1 (es) * 2005-04-14 2005-11-01 Antonio Ferreres Lopez Valvula de distribucion rotativa para motores termicos cuatro tiempos a propulsion de hidrogeno.
ITPA20100018A1 (it) * 2010-04-20 2011-10-21 Vincenzo Adamo Sistema di distribuzione a flauti.

Also Published As

Publication number Publication date
EP0086190A1 (fr) 1983-08-24

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Designated state(s): FR